JP2018135763A - Vertical pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To cool a motor which generates heat in a vertical pump.SOLUTION: A vertical pump includes: a pump casing 3 having a sub passage pipe part 4a provided with a first flange 13 defining an opening 4 above a suction port 1; a main shaft 5 extending within the pump casing 3 in a substantially vertical direction; an impeller 6 fixed to the main shaft 5 at a lower part; a motor part 11 which is disposed on the first flange 13 and rotates the main shaft 5; a heat exchanger 12 provided near the opening 4; and a second flange 15 which is provided at the motor housing 8 and/or the heat exchanger 12 and fastened to the first flange 13. Water can be flown out between the first flange 13 and the second flange 15. Part of pumping water flows out to the outside between the sub passage pipe part 4a and the housing 8 to generate water flow below the heat exchanger 12, improve the heat exchange efficiency of the heat exchanger 12, and improve motor 10 cooling performance of the heat exchanger 12.SELECTED DRAWING: Figure 1A

Description

  It relates to a vertical shaft pump.

The pump pumps up the impeller by rotating it with a driving machine such as a motor. For this reason, the drive unit continuously generates heat during the pump operation, and thus needs to be cooled. There are roughly two types of cooling methods for driving machines used for pumps installed on land, that is, air cooling by a fan using the rotation of a driving rotary shaft and water cooling using a cooler. However, a drive machine usually installed on land cannot be driven if it is submerged.
Therefore, it is considered to install a high place so that the drive unit will not be submerged even if water enters the pump building due to river flooding due to tsunami, storm surge and local heavy rain. Specifically, the floor level where the pump and the drive unit are installed is raised, or the ceiling of the floor where the pump is installed is raised so that the drive unit can be placed at a high level with a platform for the drive unit above the pump. This has been dealt with by newly providing a floor for installing the drive unit above the floor on which the pump is installed. However, the cost of construction has increased due to the size of the building.

JP 2001-304163 A Patent No. 5552402

In order to solve the above-mentioned background art, Patent Document 1 attempts to prevent water from entering the motor around the pump equipment. However, if the motor is actually submerged, the air-cooled fan with the motor will stop functioning. Even in such a situation, even if the motor can be cooled with water around the submerged motor, the pump is temporarily installed. The water that flows into the room is not fluid and the volume of water that enters the pump installation room is limited, so the water around the motor gradually warms due to the continuous heat generation of the motor, and the temperature gradient with the motor decreases. As a result, the amount of heat transfer will eventually decrease and the motor may stop.
On the other hand, in Patent Document 2, a heat exchanger in which a motor frame is surrounded by a cooling liquid, a cooling liquid is circulated by a built-in cooling water circulation impeller, and a heat exchanger for cooling the cooling water by pumping water is installed below the motor. A pump technology in which an attached motor is mounted directly above the pump is disclosed. However, in the disclosed technology, since the water-resistant motor is attached to the pump in a watertight state, the lower surface of the heat exchanger (the pumping water contact surface) is located above the main flow path of the pump and away from the main flow path. There was a problem that pumped water stagnate, and foreign matter having a specific gravity smaller than that of air or water is likely to adhere, resulting in a decrease in the performance of the heat exchanger. In addition, when the bottom surface of the heat exchanger is corrugated in order to increase the heat transfer area of the heat exchanger, air and foreign matter collected in the corrugated groove are difficult to be discharged to the discharge port side, and even if the impeller has a back blade In addition, even if a flow in the circumferential direction is generated below the heat exchanger, air and foreign matters having a specific gravity smaller than that of water gather at the shaft center, and therefore there is a high possibility that they will not be discharged well. This invention is made | formed in view of such a problem, The subject is improving the performance of a heat exchanger, and providing the pump which can fully cool a motor.

According to one aspect of the present invention, there is provided a pump casing that guides water from a suction port facing downward to a discharge port facing sideward, and a first flange that defines an opening is provided above the suction port. A pump casing having a sub-flow pipe section; a main shaft extending substantially vertically in the pump casing; and an impeller fixed to the main shaft at a lower portion in the pump casing;
A motor housing disposed on the first flange; an output shaft coupled to the main shaft from the motor housing through the first flange; and a motor provided in the motor housing for rotating the main shaft. A first motor portion, a heat exchanger provided in the vicinity of the opening, and a second flange provided in the motor housing and / or the heat exchanger and fastened to a first flange. A vertical shaft pump is provided in which water can flow out from between the flange and the second flange.

When the vertical pump is stopped, air is present in the pump casing. When the pump is started, most of the air in the pump casing escapes from the air vent valve installed near the discharge port, but part of the air goes to the sub-flow pipe section of the pump casing and accumulates on the lower surface of the heat exchanger. . Furthermore, the water pumped up by the impeller contains fine bubbles. Most of the fine bubbles go to the discharge port together with the pumped water, but some of them flow into the sub-flow channel and accumulate on the lower surface of the heat exchanger.
Here, the thermal conductivities at room temperature and normal pressure of copper used in water, air, and general heat exchangers are 0.61 [W / (m · K)] and 0.026 [W / (m · K), respectively. )] And greatly different from about 370 [W / (m · K)]. Furthermore, when an air reservoir (air layer) is interposed on the lower surface of the heat exchanger, heat transfer between water and the air layer, heat conduction between the air layer and heat transfer between the air and the heat exchanger, and a heat resistance element Since the heat transfer coefficient between the air and the heat exchanger is smaller than the heat transfer coefficient between the water and the heat exchanger, the heat transfer rate at the heat exchanger heat transfer surface is greatly reduced. As a result, the heat exchange efficiency is greatly reduced.
In particular, when the vicinity of the heat exchanger has a watertight structure, the pumped water is stagnated, and the flow velocity below the heat exchanger is slower than the main flow velocity from the suction port toward the discharge port. Therefore, since the heat transfer coefficient on the lower surface of the heat exchanger is small, it becomes a factor of reducing the heat passage rate of the heat exchanger, and further reduces the heat exchange efficiency.
The present invention has been made in view of the above situation, and by allowing a part of pumped water to flow out from between the first flange of the pump casing and the second flange of the motor unit, in the vicinity of the lower surface of the heat exchanger. Increase the heat exchange performance of the heat exchanger by actively generating water flow, eliminating air and foreign matters, and improving the heat passage rate, and sufficiently cooling the motor by enhancing the motor cooling performance of the heat exchanger It is an object of the present invention to provide a vertical shaft pump having a structure capable of achieving the above. In the present specification, pumped water and water are not limited to H ₂ O and mean a liquid to be pumped up by a pump.

A groove through which water can flow out may be provided in the first flange.
A part of the pumped water flows out of the groove to the outside, actively generating a water flow near the bottom of the heat exchanger, and improving the heat exchange efficiency of the heat exchanger, thereby improving the motor cooling performance of the heat exchanger. The motor can be sufficiently cooled. One or a plurality of grooves can be provided. The shape of the groove can be set as appropriate. In order to easily remove air accumulated on the lower surface of the heat exchanger, the upper surface of the groove is preferably at the same level as the lower surface of the heat exchanger or higher than the lower surface of the heat exchanger.

A groove through which water can flow out may be provided in the second flange.
A part of the pumped water flows out of the groove to the outside, actively generating a water flow near the lower surface of the heat exchanger, increasing the heat exchange efficiency by the heat exchanger, improving the motor cooling performance of the heat exchanger, The motor can be sufficiently cooled. One or a plurality of grooves can be provided. The shape of the groove can be set as appropriate. The upper surface of the groove is preferably at the same level as the lower surface of the heat exchanger or higher than the lower surface of the heat exchanger.

The upper surface of the groove may be at the same level as the lower surface of the heat exchanger or higher than the lower surface of the heat exchanger.
Since the upper surface of the groove is at the same level as the lower surface of the heat exchanger or higher than the lower surface of the heat exchanger, air accumulated on the lower surface of the heat exchanger due to buoyancy, foreign matter with a lower specific gravity than pumped water, etc. It becomes easy to move to the groove that leads to the outside along with the flow toward the groove generated on the lower surface, and once it enters the groove, it does not return to the lower surface of the heat exchanger that is lower than the upper surface of the groove by buoyancy. Since it is discharged, it is possible to prevent the heat exchanger from staying near the lower surface of the heat exchanger, and it is possible to prevent the heat exchange efficiency of the heat exchanger from being lowered due to air, foreign matter, etc. remaining on the lower surface of the heat exchanger. The groove is preferably opened to the atmosphere.

You may provide the drain pipe connected to the said groove | channel and open | released toward the downward direction.
As a part of the pumped water passes outside from the groove and drain pipe, water flow is actively generated near the lower surface of the heat exchanger, and the heat exchange efficiency by the heat exchanger is improved, so that the motor cooling performance of the heat exchanger And the motor can be sufficiently cooled. It is preferable that the other end of the drain pipe is provided sufficiently above the liquid level in the suction water tank. The other end of the drain pipe is preferably located above the highest water level at which the pump can be operated. Moreover, it is preferable that the curved part in the middle of the drain pipe has a curvature as large as possible so that a linear foreign substance is not caught in the part.

A flow sensor may be provided in the drain pipe.
By measuring the flow rate in the drain pipe with the flow sensor, it is possible to monitor the clogging of the grooves, the drain pipe, and the operation status of the pump. In order to prevent the flow rate sensor from losing its function due to water immersion on the pump installation floor, it is preferable to select a waterproof type when installing the flow rate sensor below a water level where water immersion is assumed.

A flow path branched from the drain pipe, a first valve provided downstream from the branch point of the drain pipe with the flow path, a second valve provided in the flow path, and provided in the flow path The flushing pump may be provided, and foreign matter accumulated in the vicinity of the groove in the drain pipe may be poured into the pump casing. Foreign matter accumulated in the drain pipe, in the groove, or in the vicinity of the groove in the drain pipe can be removed.
The pump installation floor of the pump station is often unattended, and it is preferable that the valve is electrically operated so that the valve can be opened and closed by operating or controlling from the pump operation room or remotely. In order to prevent the electric valve from losing its function due to water immersion on the pump installation floor, it is preferable to select a waterproof type when installing a valve or a flushing pump below the water level where water immersion is assumed.
The second valve is preferably a valve having a large valve opening cross section when the valve is open, such as a gate valve, a ball valve, or a funnel valve, because pumped water containing foreign matter or the like always passes during pump operation.
When the drain pipe is clogged with foreign matter or the like, the first valve is closed, the second valve is opened, water is sent to the drain pipe side through the flow path by the flushing pump, and the water flows backward from the drain pipe to the groove. Clogging of drainage pipes, grooves and the like is eliminated by pouring foreign matter into the pump casing by this water flow. The flushing pump discharges a pressure sufficiently higher than the pressure in the sub-flow pipe section in consideration of the pipe loss up to the sub-flow pipe section so that the vertical pump can back flow even when it is in operation. It is preferable to select a pump that can be used. It is preferable that the inner diameter of the drain pipe is larger than the particle size that can pass through the groove so that foreign matter or the like that has passed through the groove is not clogged in the drain pipe. In many pump stations, there is a dust removal facility before water flows into the suction tank, and large foreign objects are removed by the dust remover. Therefore, the particle size of foreign matters contained in the water pumped up by the pump can be based on the screen width of the dust remover.

The lower surface of the heat exchanger may be inclined so as to increase in the vertical direction toward the groove.
Foreign matter having a specific gravity smaller than that of air and water also has the effect of buoyancy, making it easier to travel along the inclined lower surface of the heat exchanger in the direction of the groove at a higher position. At the same time, it becomes easy to discharge from the groove. Thereby, it is possible to more effectively prevent air, foreign matter, and the like from accumulating on the lower surface of the heat exchanger.

You may have a crushing cutter rotated with the said main axis | shaft, and the fixed blade provided in the groove | channel vicinity.
The crushing cutter rotates with the rotation of the spindle, and the crushing cutter blade and the fixed blade crush or remove foreign matter in the vicinity of the groove to prevent or eliminate clogging of the groove and the drain pipe. It is desirable that the tip of the crushing cutter is inclined from the upper side to the lower side. Even when the foreign matter cannot be crushed, the foreign matter can be removed from the groove. The fixed blade is provided in the vicinity of the groove. Preferably, the fixed blade is provided at the edge of the groove. Preferably, the fixed blade is provided in a portion in close contact with the groove. The shape of the fixed blade can be selected as appropriate.

A partition member provided below the heat exchanger in the sub-flow channel pipe portion may be provided, and water may pass from the partition member to the heat exchanger side.
As a means for allowing water to pass, it is preferable to provide a hole-shaped or gap-shaped water passage portion in the partition member. One or a plurality of water passing portions can be provided. The shape and size of the water flow portion can be designed as appropriate, but it is preferable to design the water flow portion so as not to be blocked by foreign matter contained in the pumped water. A part of the pumped water flows into a gap formed between the lower surface of the heat exchanger and the upper surface of the partition member through the water passage, and is finally discharged to the outside from the groove. By setting the gap between the partition member and the heat exchanger to a suitable size, the flow in the vicinity of the lower surface of the heat exchanger can be increased more than when there is no partition member. Since the heat transfer rate on the lower surface of the heat exchanger is improved and the heat exchange efficiency of the heat exchanger is increased, the motor cooling performance of the heat exchanger can be improved. The gap size between the upper surface of the partition member and the lower surface of the heat exchanger is preferably within 50, 40, 30, 20, 10, 5 centimeters, and most preferably within 3 centimeters. It can design suitably so that the foreign material etc. which are contained in pumping water may not get caught. Preferably, a water flow portion is provided in a semicircle on the opposite side of the groove to the main shaft of the partition member. Most preferably, a water flow portion is provided on the opposite side of the groove to the main shaft. A part of the pumped water flows through a gap formed between the lower surface of the heat exchanger and the upper surface of the partition member, and is discharged to the outside from the groove. Below the heat exchanger, the water flow distance can be increased and the heat transfer area of the heat exchanger can be effectively utilized. Therefore, by increasing the heat exchange efficiency of the heat exchanger, the motor cooling of the heat exchanger Performance can be increased.

Water may be able to pass from the partition member to the heat exchanger side on the opposite side of the groove with respect to the main shaft.
Below the heat exchanger, the water flow distance can be increased and the heat transfer area of the heat exchanger can be effectively utilized. Therefore, by increasing the heat exchange efficiency of the heat exchanger, the motor cooling of the heat exchanger Performance can be increased.

  The pump can cool the motor efficiently.

1 is a vertical sectional view showing a pump according to a first embodiment of the present invention. 1 is a vertical sectional view showing a pump according to a first embodiment of the present invention. 1 is a vertical sectional view showing a pump according to a first embodiment of the present invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 1st Embodiment of this invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 1st Embodiment of this invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 1st Embodiment of this invention. It is a horizontal sectional view showing the pump concerning a 1st embodiment of the present invention. It is a horizontal sectional view showing the pump concerning a 1st embodiment of the present invention. It is a vertical sectional view showing a pump according to a second embodiment of the present invention. It is a horizontal sectional view showing a pump concerning a 2nd embodiment of the present invention. It is a horizontal sectional view showing a pump concerning a 2nd embodiment of the present invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 2nd Embodiment of this invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 2nd Embodiment of this invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 2nd Embodiment of this invention. It is a vertical sectional view showing a pump according to a third embodiment of the present invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 3rd Embodiment of this invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 3rd Embodiment of this invention. It is a schematic sectional drawing of the heat exchanger periphery of the pump which concerns on 3rd Embodiment of this invention. It is a horizontal sectional view showing a pump concerning a 3rd embodiment of the present invention. It is a horizontal sectional view showing a pump concerning a 3rd embodiment of the present invention. It is a vertical sectional view showing a pump according to a fourth embodiment of the present invention. It is a vertical sectional view showing a pump according to a fifth embodiment of the present invention. It is a vertical sectional view showing a pump according to a fifth embodiment of the present invention. It is a horizontal sectional view showing a pump concerning a 5th embodiment of the present invention. It is a horizontal sectional view showing a pump concerning a 5th embodiment of the present invention. It is a horizontal sectional view showing a pump concerning a 5th embodiment of the present invention. It is a vertical sectional view showing a pump according to a sixth embodiment of the present invention. It is a vertical sectional view showing a pump according to a seventh embodiment of the present invention. It is a vertical sectional view showing a pump concerning an 8th embodiment of the present invention. It is a horizontal sectional view showing a pump concerning an 8th embodiment of the present invention. It is an enlarged view which shows the rotary blade and fixed blade of the pump which concern on 8th Embodiment of this invention. It is a vertical sectional view showing a pump according to a ninth embodiment of the present invention. It is a vertical sectional view showing a pump according to a tenth embodiment of the present invention. It is a vertical sectional view showing a pump according to an eleventh embodiment of the present invention. It is a vertical sectional view showing a pump according to a twelfth embodiment of the present invention. It is a vertical sectional view showing a pump according to a thirteenth embodiment of the present invention.

  Embodiments according to the present invention will be specifically described below with reference to the drawings.

(First embodiment)
FIG. 1A is a vertical sectional view showing a pump according to a first embodiment of the present invention.

  This pump is, for example, a vertical shaft pump disposed in a drainage station, and by rotating the impeller 6, the water in the suction water tank 16 is pumped and drained into the discharge water tank. The pump includes a pump casing 3, a main shaft 5, an impeller 6, a motor unit 11, a heat exchanger 12, and a drain pipe 17.

  The pump casing 3 has a suction port 1 facing downward and a discharge port 2 facing a side above the pump (horizontal direction in the example of the figure), and a bend pipe section above the suction port 1. There is a sub-flow passage pipe portion 4a that branches off from 4b and extends in the vertical direction, and a first flange 13 that defines an opening 4 is provided on the upper surface of the sub-flow passage pipe portion 4a.

  The pump draws water from the suction water tank 16 through the suction port 1 by rotating the impeller 6, guides it to the discharge port 2 through the bend pipe portion 4 b, and drains it into the discharge water tank. A part of the water pumped up by sucking water in the suction water tank 16 from the suction port 1 flows into the sub-flow pipe part 4a branched from the bend pipe part 4b and reaches the opening 4, and as described later, the motor part. 11 is cooled.

  The axis of the rotation shaft (the output shaft 9 of the motor 10 and the main shaft 5 in which the lower end side of the output shaft 9 is connected by the underwater shaft joint 40) substantially coincides with the center line of the pump casing 3 and extends in the vertical direction. An impeller 6 is fixed to the main shaft 5 at the lower part of the pump casing 3. As the main shaft 5 rotates, water is pumped up from the suction port 1.

The motor unit 11 includes a motor housing 8, an output shaft 9, a motor 10, and the like.
The motor housing 8 accommodates the output shaft 9 and the motor 10 inside. The motor housing 8 and / or the heat exchanger 12 has a second flange 15 for attaching to the first flange 13 on the upper surface of the sub-flow pipe portion 4a of the pump.
In FIG. 1A, the second flange 15 is provided in the motor housing 8, but may be provided in the heat exchanger 12 as shown in FIG. 1B. Moreover, you may provide in both the motor housing 8 and the heat exchanger 12 like FIG. 1C.
A motor housing 8 is arranged so as to be located on the opening 4 in the pump casing 3. A cooling member such as a cylindrical water jacket may be provided on the side surface of the motor housing 8.

  The output shaft 9 extends in the vertical direction from the inside of the motor housing 8, passes through the heat exchanger 12, and reaches the pump casing 3. The lower end of the output shaft 9 is connected to the upper end of the main shaft 5 by an underwater shaft joint 40. Therefore, the output shaft 9 and the main shaft 5 can rotate together.

  The motor 10 is inside the motor housing 8 and rotates the output shaft 9. The main shaft 5 is also rotated by the rotation of the output shaft 9. Although the motor 10 generates heat when the output shaft 9 is rotated, according to the present embodiment, the heat exchange efficiency of the heat exchanger 12 is increased, and the motor cooling performance of the heat exchanger 12 is improved. Can cool well. This point will be described in detail later.

  The heat exchanger 12 is provided below the motor unit 11. The heat exchanger 12 has a cylindrical shape with an opening at the center, and the output shaft 9 passes through the opening in a rotatable manner. Further, an appropriate waterproof measure, for example, a mechanical seal is provided in the through portion of the output shaft 9 of the heat exchanger 12 so that water from the sub-flow channel pipe portion 4a does not enter the motor portion 11. Yes.

  The upper surface of the heat exchanger 12 receives the heat of the motor 10. On the other hand, the water drawn from the suction water tank 16 contacts the lower surface of the heat exchanger 12. Therefore, the heat exchanger 12 can cool the motor 10 by exchanging heat between the motor 10 and the water pumped from the suction water tank 16. The motor 10 may be directly cooled by the heat exchanger 12, or indirectly cooled by circulating cooling water around the motor by an appropriate method such as a cooling water circulation impeller built in the motor unit 11. Structure may be sufficient.

  As one of the features of the present embodiment, there is a gap between the first flange 13 on the upper surface of the sub-flow pipe portion 4a and the second flange 15 provided in the motor portion 11 and / or the heat exchanger 12 facing each other. The part is not in a watertight state, and the water in the sub-channel pipe part 4a can flow out to the outside. More specifically, a groove 14 through which water can pass is provided in the first flange 13, and a drain pipe 17 is connected to the tip of the groove 14. The drain pipe 17 is curved halfway, and the tip is open to the atmosphere in the suction water tank 16. Hereinafter, the relationship between the arrangement of the heat exchanger 12 and the grooves 14 will be described in detail.

  2A to 2C are schematic cross-sectional views around the heat exchanger 12. When the groove 14 is provided in the first flange 13, it is desirable that the lower surface of the heat exchanger 12 be at the same level or below the lower surface of the second flange 15. That is, it is desirable that the upper surface of the groove 14 be at the same level as the lower surface of the heat exchanger 12 (FIG. 2A) or at a higher position (FIG. 2B). When the upper surface of the groove 14 is at a position lower than the lower surface of the heat exchanger 12 (FIG. 2C), air bubbles contained in the air in the pump casing 3 when the pump is started or pumped water during the pump operation This is because foreign matter having a specific gravity smaller than that of water tends to accumulate, and in particular, it tends to stay at a position surrounded by a broken line near the groove 14.

  FIG. 3A is a view of the first flange 13 of the pump as viewed from above, and FIG. 3B is a view of the second flange 15 of the motor unit 11 as viewed from below. As shown in FIG. 3A, the groove 14 extends from the inner surface of the sub-flow channel pipe portion 4 a to the outer peripheral end of the first flange 13, and a drain pipe 17 is connected to the tip of the groove 14. Thereby, the water from the subchannel pipe 4a can pass outside the first flange 13, that is, outside the pump.

  As shown in FIGS. 3A and 3B, the first flange 13 and the second flange 15 are respectively provided with bolt holes, and the first flange 13 and the second flange 15 are fastened by bolts. Water between the first flange 13 and the second flange 15 is stopped by an appropriate method for those skilled in the art. In FIG. 3A, a rubber string groove is provided radially inward from the bolt hole of the first flange 13, a rubber string 41 is fitted, an O ring groove is provided in the piping flange 34, an O ring 42 is fitted, and the rubber string is fitted. Both ends of 41 are abutted against the O-ring 42 and water is stopped. The elastic cord 41 may be provided on the second flange 15. Alternatively, the water may be stopped by a combination of sheet gaskets without providing rubber string grooves or O-ring grooves. Alternatively, either the first flange 13 or the second flange 15 is provided with a rubber string groove in the same manner as described above, a rubber string is fitted, the piping flange 34 is not provided with an O-ring groove, and a rubber gasket is used. Water may be stopped by butting both ends of the string against the sheet gasket. Alternatively, the first flange 13 and the second flange 15 are not provided with rubber string grooves, but a sheet gasket is used, the piping flange 34 is provided with an O-ring groove, the O-ring is fitted, and the combination of the seat gasket and the O-ring is stopped. Also good. The drain pipe 17 is connected to a pipe flange 34.

  In FIG. 1, the groove 14 and the drain pipe 17 are provided in the opposite direction to the discharge port 2, that is, at a position opposite to 180 degrees, but the position of the groove 14 is not particularly limited. It can be provided at an appropriate position such as a position, and two or more grooves 14 and a drain pipe 17 may be provided. When the lower surface of the heat exchanger 12 is a corrugated type and a plurality of grooves extending in parallel with each other are formed, foreign matter having a specific gravity smaller than air or water stays in the grooves due to buoyancy. It is desirable to provide the groove 14 and the drain pipe 17 on one or both ends of the groove on the lower surface of the heat exchanger 12 so that they can be guided to the groove 14 and discharged by the water flow generated on the lower surface of the heat exchanger 12.

  The pump described above operates as follows. When the output shaft 9 rotates, the main shaft 5 connected to the output shaft 9 by the underwater shaft joint 40 rotates, and the impeller 6 fixed to the main shaft 5 rotates. Thereby, water is pumped up from the suction inlet 1. Most of the pumped water is drained from the discharge port 2 through the bend pipe portion 4b. The remaining part of the pumped water reaches the lower part of the opening 4 through the sub-flow channel pipe part 4a. This water cools the heat of the motor 10 by the heat exchanger 12. Since the water in the subchannel pipe portion 4 a is pressurized by the impeller 6, the water near the lower surface of the heat exchanger 12 is then pushed out into the groove 14 near the lower surface of the heat exchanger 12 in the form of the drain pipe 17. Drained from. Therefore, even when bubbles are mixed in the pumped water or foreign matter having a specific gravity smaller than that of water is mixed, the foreign matter having a specific gravity lower than that of the bubbles and water due to the water flow generated near the lower surface of the heat exchanger 12 is It is carried to the groove 14 and exhausted and discharged from the drain pipe 17. In order to suitably exhaust and discharge, it is desirable to determine the groove cross-sectional area and the pipe diameter so that the flow velocity in the groove 14 and the drain pipe 17 is 1 m / s or more.

  If the mounting surface (first flange 13) on the upper surface of the sub-flow pipe portion 4a of the pump casing 3 and the mounting surface (second flange 15) of the motor unit 11 are in a watertight state, the water below the heat exchanger 12 Since the heat transfer rate is reduced, the heat transfer rate of the heat exchanger 12 is reduced. In addition, air bubbles in the pump casing 3 at the time of pump start-up and air bubbles mixed in the pumped water during pump operation accumulate on the lower surface of the heat exchanger 12, and air pockets adhere, or foreign matter having a specific gravity smaller than that of water. If such is attached, a layer having a low heat transmission rate is formed on a part or the whole of the lower surface of the heat exchanger 12, and the heat exchange efficiency of the heat exchanger 12 is significantly reduced. Both of these adverse effects can prevent the motor 10 from being sufficiently cooled.

  On the other hand, in the present embodiment, the mounting surface (first flange 13) on the upper surface of the sub-flow pipe portion 4a of the pump casing 3 and the mounting surface (second flange 15) of the motor unit 11 are not made watertight. The first flange 13 is provided with a groove 14, and a part of the pumped water is positively discharged from the groove 14 and the drain pipe 17 connected to the groove 14. As a result, a water flow is generated in the vicinity of the lower surface of the heat exchanger 12 to prevent the formation of air pockets on the lower surface of the heat exchanger 12 and adhesion of foreign matter having a specific gravity smaller than that of water, and the flow in the vicinity of the lower surface of the heat exchanger is increased. Therefore, heat exchange is promoted and the motor 10 can be sufficiently cooled.

(Second Embodiment)
In the first embodiment described above, the groove 14 is provided in the first flange 13 of the sub-flow passage pipe portion 4 a of the pump casing 3. On the other hand, in the second embodiment described below, the groove 14 is provided in the second flange 15 below the motor unit 11. Hereinafter, a description will be given focusing on differences from the first embodiment.

  FIG. 4 is a vertical sectional view showing a pump according to the second embodiment of the present invention. 6A to 6C are schematic cross-sectional views around the heat exchanger. When the groove 14 is provided in the second flange 15, the upper surface of the groove 14 is preferably at the same level (FIG. 6A) as the lower surface of the heat exchanger 12 or at a higher position (FIG. 6B). When the upper surface of the groove 14 is lower than the lower surface of the heat exchanger 12 (FIG. 6C), foreign matter having a specific gravity smaller than that of air or water tends to accumulate on the lower surface of the heat exchanger 12, and is surrounded by a broken line near the groove 14 in particular. This is because air stays at the position. FIG. 5A is a view of the first flange 13 of the pump as viewed from the vertically upward direction, and FIG. 5B is a view of the second flange 15 of the motor unit 11 as viewed from the vertically downward direction. As shown in FIG. 5B, the groove 14 extends from the inner diameter of the second flange 15 to the outer peripheral end, and a drain pipe 17 is connected to the tip of the groove 14. Thereby, the water of the subchannel pipe part 4a can flow out to the outside of the second flange 15, that is, the outside of the pump.

  Thus, in this embodiment, since the groove 14 is provided in the second flange 15, a water flow is generated in the vicinity of the lower surface of the heat exchanger 12, and an air pocket is formed on the lower surface of the heat exchanger 12 or a foreign matter having a specific gravity smaller than that of water. Since the flow near the lower surface of the heat exchange is accelerated, the heat exchange is promoted and the motor 10 can be sufficiently cooled.

(Third embodiment)
In the third embodiment to be described next, a groove 14 straddling the first flange 13 of the sub-flow passage pipe portion 4 a of the pump casing 3 and the second flange 15 of the motor housing 8 is provided.

  FIG. 7 is a vertical sectional view showing a pump according to the third embodiment of the present invention. 8A to 8C are schematic cross-sectional views around the heat exchanger. When the groove 14 is provided in the first flange 13 and the second flange 15, the upper surface of the groove 14 is preferably at the same level as the lower surface of the heat exchanger 12 (FIG. 8A) or at a higher position (FIG. 8B). When the upper surface of the groove 14 is lower than the lower surface of the heat exchanger 12 (FIG. 8C), foreign matter having a specific gravity smaller than that of air or water tends to accumulate on the lower surface of the heat exchanger 12, and is surrounded by a broken line near the groove 14 in particular. This is because air stays at the position. Moreover, FIG. 9A is the figure which looked at the 1st flange 13 of the pump from the perpendicular upper direction, and FIG. 9B is the figure which looked at the 2nd flange 15 of the motor part 11 from the perpendicular downward direction. As shown in FIGS. 9A and 9B, the groove 14 is provided across both the first flange 13 and the second flange 15.

  Thus, in this embodiment, since the groove | channel 14 straddling the 1st flange 13 and the 2nd flange 15 is provided, a water flow arises in the heat exchanger 12 lower surface vicinity, heat exchange is accelerated | stimulated and the motor 10 can fully be cooled.

(Fourth embodiment)
The fourth embodiment to be described next relates to the shape of the heat exchanger 12.

FIG. 10 is a vertical sectional view showing a pump according to the fourth embodiment of the present invention.
The lower surface 18 of the heat exchanger 12 is inclined so as to increase in the vertical direction toward the groove 14. This pump operates as follows. The water pumped up from the suction port 1 by the operation of the motor 10 and the rotation of the impeller 6 is directed upward in the pump casing 3, and part of the water flows into the sub-flow pipe part 4 a branched from the bend pipe part 4 b. It reaches the lower surface 18 of the exchanger 12. Since the lower surface 18 of the heat exchanger 12 is formed in an inclined shape, a part of the pumped water that hits the lower surface 18 of the heat exchanger 12 is guided to the groove 14. Further, bubbles contained in the pumped water, foreign matters having a specific gravity smaller than that of water are added to the momentum of the water flow toward the groove 14 formed below the lower surface 18 of the heat exchanger 12 and buoyancy is also added. It becomes easy to move toward the groove 14 along the inclination of the lower surface 18, and it becomes easier to discharge from the groove 14 together with pumping.

  Thus, in this embodiment, since the lower surface 18 of the heat exchanger 12 is inclined so as to become higher toward the groove 14, it is possible to further prevent adhesion of air pockets and foreign matters to the lower surface 18 of the heat exchanger 12. The heat exchange efficiency of the heat exchanger 12 can be maintained.

  In addition, what is necessary is just to make it the lower surface of the heat exchanger 12 become low, so that it leaves | separates from the groove | channel 14 when the groove | channel 14 is provided in one place. On the other hand, when the two grooves 14 are provided 180 degrees opposite to the main shaft 5, the lower surface of the heat exchanger 12 is the lowest in the vicinity of the main shaft 5 and becomes higher toward the two grooves 14 toward the outer side in the radial direction. It is desirable to do so.

(Fifth embodiment)
In a fifth embodiment to be described next, a partition member is provided below the heat exchanger 12.

  FIG. 11A is a vertical sectional view showing a pump according to a fifth embodiment of the present invention. The present pump includes a partition member 19 provided below the heat exchanger 12 in the sub-flow pipe portion 4a of the pump casing 3, and a horizontal sectional view thereof is shown in FIG. The center of the partition member 19 is open, and the output shaft 9 passes therethrough. Further, in the present embodiment, the outline of the partition member 19 has a shape obtained by cutting out a part of a circle. In this case, the gap between the sub-flow channel pipe portion 4a and the partition member 19 corresponds to the water flow portion 20. To do. A water flow portion 20 is provided in an arbitrary part of the partition member 19, whereby the water flow portion 20 through which water can pass is provided in the partition member 19. On the other hand, the other part of the partition member 19 is in contact with the inner surface of the sub-flow pipe portion 4 a of the pump casing 3 and shields the sub-flow pipe portion 4 a of the pump casing 3. It is desirable that the water flow portion 20 is provided in a semicircle opposite to the groove 14 with respect to the output shaft 9. In this embodiment, in FIG. 11A, the lower surface of the partition member 19 is horizontal, but may be inclined so as to increase in the vertical direction toward the water passing portion 20. As shown in FIG. 11B, the pumped water pumped up by the impeller 6 may be shaped to match the curvature of the bend pipe portion 4b in order to smoothly guide it to the discharge port 2. By doing so, the pump efficiency can also be improved.

  The narrower the gap between the upper surface of the partition member 19 and the lower surface of the heat exchanger 12, the faster the flow rate of the water flowing through the gap, contributing to the improvement of the heat transfer coefficient, and the bubbles, foreign matter, etc. contained in the pumped water Can be easily moved to the groove 14. The gap dimension between the upper surface of the partition member 19 and the lower surface of the heat exchanger 12 is preferably within 50, 40, 30, 20, 10, 5 centimeters, and most preferably within 3 centimeters. It can design suitably so that the foreign material etc. which are contained in pumping water may not get caught. The pump described above operates as follows. The pumped water pumped up from the suction port 1 by the operation of the motor 10 and the rotation of the impeller 6 goes upward in the pump casing 3. A part of the pumped water flows upward through the partition member 19 through the water passage 20 of the partition member 19 and flows to the outside through the groove 14. Since the gap between the upper surface of the partition member 19 and the lower surface of the heat exchanger 12 is narrow, the flow rate increases from the water passage 20 to the groove 14 below the heat exchanger 12, and heat transfer is improved, so heat exchange is performed. It is further promoted to sufficiently cool the motor 10.

  In addition, the position, shape, number, etc. of the water flow section 20 are not limited to those shown in FIG. For example, as shown in FIG. 13, the water flow portion 20 may be provided on the opposite side of the groove 14 with respect to the output shaft 9, that is, on the opposite side of 180 degrees. Further, as shown in FIG. 14 in consideration of the shape and size of the foreign matter contained in the handling liquid, the water flow portion 20 may be formed by providing a hole in the partition member 19. In any case, it is only necessary to secure a water path from the partition member 19 to the heat exchanger 12.

(Sixth embodiment)
In a sixth embodiment to be described next, a flow rate sensor is provided in the drain pipe 17.

  FIG. 15 is a vertical sectional view showing a pump according to the sixth embodiment of the present invention. The pump includes a flow sensor 21 installed at an arbitrary position of the drain pipe 17. The flow sensor 21 measures the flow rate of water flowing through the drain pipe 17. The pump installation floor of the pump station is often unattended, and it is better to be able to monitor the flow rate in the pump operation room or remotely, and the flow rate sensor 21 is preferably equipped with a transmitter. The flow sensor 21 is preferably an electromagnetic or ultrasonic sensor having no movable part and having a flow channel cross-sectional shape and a cross-sectional area of the measuring part close to a circular pipe. In the case where the flow sensor 21 is installed below a water level where flooding is assumed, it is preferable to select a waterproof type.

  When the foreign substance etc. are clogged in the groove | channel 14 or the drain pipe 17, or when the operating point of a pump changes, the flow volume of the water discharged | emitted from the drain pipe 17 will change. Therefore, by measuring the flow rate of the drain pipe 17, it is possible to monitor the clogging of the groove 14 and the drain pipe 17 and the operating state of the pump.

(Seventh embodiment)
A seventh embodiment to be described next relates to a pump provided with a flushing function.

  FIG. 16 is a vertical sectional view showing a pump according to the seventh embodiment of the present invention. This pump includes a flow path 24 branched from the drain pipe 17, a first valve 22, a second valve 23, a flushing pump 25, and a water storage tank 43. The first valve 22 is preferably a gate valve or a ball valve in which the opening area when the valve is opened is equivalent to the front and rear pipe cross-sectional areas in consideration of the passage of dust. It is preferable that fresh water is stored in the water storage tank 43, and it is preferable that a facility for replenishing the water appropriately is provided when the amount of fresh water in the water storage tank 43 decreases.

The second valve 23 is provided in the flow path 24, and when the second valve 23 is closed, the flow path of the flow path 24 is blocked. A third valve 44 may be provided between the water storage tank 43 on the flow path 24 and the flushing pump 25. The third valve 44 is normally opened, but can be closed when the flushing pump 25 is maintained or replaced.
The first valve 22 is provided on the downstream side of the branch point with the flow path 24 in the drain pipe 17. When the first valve 22 is closed, the flow path of the drain pipe 17 is blocked.
The flushing pump 25 is provided in the flow path 24. In FIG. 16, the suction side is connected to the water storage tank 43 via the third valve 44.

The normal pump operates with the first valve 22 opened and the second valve 23 closed. When the inlet (sub-channel pipe portion 4a) of the groove 14 is blocked by foreign matter or the like, or when foreign matter or the like is clogged in the groove 14, the first valve 22 is closed, the flushing pump 25 is operated, and the second valve 23 is operated. open. The flushing pump 25 receives supply of water used for flushing from an appropriate supply source such as the water storage tank 43, and feeds water into the groove 14 through the drain pipe 17. Foreign matter or the like caught at the inlet (sub-channel pipe portion 4a) of the groove 14 or foreign matter clogged in the groove 14 is returned into the pump casing 3 by the water flow from the flushing pump 25. In order to perform flushing even during pump operation, a pump that can discharge a pressure sufficiently higher than the pressure of the sub-flow pipe portion 4a is selected as the flushing pump 25 in consideration of the pipe loss up to the sub-flow pipe portion 4a. It is preferable to do. The foreign matters and the like that have returned to the pump casing 3 are gradually discharged from the discharge port 2 along the water flow toward the discharge port 2.
Flushing may be performed by assembling a program for automatically controlling the first valve 22, the second valve 23, and the flushing pump 25 so that the flushing is intermittently performed every fixed time of the pump operation. The first valve is provided when a threshold value is provided for the flow rate value by the flow rate sensor in combination with the form, and when blockage near the groove 14 is suspected, or when blockage is predicted in the future by flow rate trend management analysis as a preventive measure. 22 may be implemented by building a program for automatically controlling the second valve 23 and the flushing pump 25.

  When a land pump is selected as the flushing pump 25, it is preferably installed at a high position so as not to be submerged in any case. Although not shown, a submersible pump may be selected as the flushing pump 25 and installed in the suction water tank 16. In this case, since the water in the suction water tank 16 can be used as flushing water, it is not necessary to provide the third valve 44 and the water storage tank 43. In this case, a strainer may be provided in the flushing pump 25 so as to prevent troubles in the submersible pump due to foreign matter suction or foreign matters from the flushing pump 25 to the drain pipe 17.

  Further, the inner diameter of the drain pipe 17 is preferably larger than the particle diameter that can pass through the groove 14. By doing so, even if a clogging due to foreign matter or the like occurs, it is limited to the vicinity of the inlet of the groove 14 or within the groove 14, and is therefore easily removed by the flushing pump 25.

(Eighth embodiment)
In an eighth embodiment to be described next, crushing means is provided.

  FIG. 17 is a vertical sectional view showing a pump according to the eighth embodiment of the present invention. FIG. 18A is a horizontal sectional view showing the crushing means 28. This pump includes a crushing means 28 having a crushing cutter 26, a rotary blade 45 and a fixed blade 27. FIG. 18A is a horizontal sectional view around the crushing cutter 26 of the pump.

  One end of the crushing cutter 26 is fixed to the output shaft 9 (or the main shaft 5), and the other end extends in the sub-flow channel portion 4a of the pump casing 3 to the vicinity of the inner surface of the sub-flow channel tube portion 4a. The crushing cutter 26 can rotate as the output shaft 9 rotates. The number of crushing cutters 26 is not particularly limited.

  The rotary blade 45 is fixed to the tip of the crushing cutter 26. The fixed blade 27 is fixed to the vicinity of the groove 14, for example, the edge of the groove 14, preferably a portion in close contact with the groove 14.

  The crushing means 28 operates as follows. The crushing cutter 26 rotates as the output shaft 9 rotates. The crushing cutter 26 and the fixed blade 27 crush foreign matters near the groove 14. FIG. 18B is an enlarged view of the positional relationship between the rotary blade 45 and the fixed blade 27 of the crushing cutter 26 as seen from the axial center outward in the radial direction. It is preferable that the circumferential front edge of the rotary blade 45 attached to the crushing cutter 26 is inclined from the upper side to the lower side so as to become thinner toward the lower side. The rotary blade 45 moves in the direction of the arrow in FIG. 18B (from the left side to the right side) as the crushing means 28 rotates. By forming the rotary blade 45 in an inclined shape, even if the foreign matter caught near the groove 14 cannot be crushed by the rotary blade 45 and the fixed blade 27, the foreign matter etc. can be removed below the groove 14. The pump can be prevented from stopping due to excessive torque. The small crushed foreign matter or the like is discharged from the groove 14 or is gradually discharged from the discharge port 2 on the water flow toward the discharge port 2. Thereby, the dust etc. near the groove 14 can be crushed or removed, and the clogging of the groove 14 and the drain pipe 17 can be prevented. The inner diameter of the drain pipe 17 is preferably larger than the particle diameter that can pass through the groove 14.

(Ninth embodiment)
In a ninth embodiment to be described next, a temperature sensor is provided.

  FIG. 19 is an enlarged vertical sectional view of the motor unit 11 according to the ninth embodiment of the present invention. The motor unit 11 is provided with a water jacket 46 for enclosing a circulating coolant 29 that cools the motor 10 around the housing 8, and circulates the coolant 29 between the motor unit 11 and the heat exchanger 12. It is the motor 10 with a heat exchanger of the structure provided with this impeller. And the motor part 11 is provided with the temperature sensor 30a provided in the flow-path part of the circulating cooling liquid 29 immediately after being cooled with the heat exchanger 12. FIG. The temperature sensor 30a is, for example, a thermocouple or a resistance temperature detector, and may be attached to the jacket surface or the coolant side surface of the heat exchanger 12, but the temperature of the circulating coolant 29 is directly measured. It is desirable to be able to measure. In order to prevent the temperature sensor 30a from losing its function due to water immersion on the pump installation floor, it is preferable to select a waterproof type when the temperature sensor 30a is installed below the water level where water immersion is assumed.

  In the motor 10 with a heat exchanger, the circulating coolant 29 is cooled by exchanging heat with pumped water in the heat exchanger 12. The circulating coolant 29 cooled in the heat exchanger 12 circulates in the motor unit 11 and heat-exchanges with the motor 10 to cool the motor 10, and the circulating coolant 29 is heated. The circulating coolant 29 repeats this cooling cycle.

  By measuring the temperature of the circulating coolant 29 cooled by the temperature sensor 30a, it is possible to monitor whether the cooling cycle by the circulating coolant 29 is operating normally. For example, if the measured temperature exceeds a predetermined value, it can be seen that some abnormality has occurred in the cooling cycle.

(Tenth embodiment)
A tenth embodiment to be described next is a modification of the ninth embodiment, and compares the temperature of the circulating coolant 29 and the temperature of pumped water using a temperature sensor.

  FIG. 20 is an enlarged vertical sectional view of the motor unit 11 according to the tenth embodiment of the present invention. This pump includes a temperature sensor 30 b provided on the motor part side of the heat exchanger 12 and a temperature sensor 30 c provided in the sub-flow pipe part 4 a of the pump casing 3. The temperature sensor 30 b measures the temperature of the circulating coolant 29 immediately after being cooled by the heat exchanger 12. On the other hand, the temperature sensor 30c measures the temperature of the pumped water.

  In the motor 10 with the heat exchanger 12, the circulating coolant 29 is cooled by heating the motor 10, and is cooled by exchanging heat with pumped water in the heat exchanger 12. When the cooling efficiency of the circulating cooling liquid 29 by the heat exchanger 12 is lowered due to air or foreign matter adhering to the lower surface 18 of the heat exchanger 12, the temperature difference between the circulating cooling liquid 29 and pumped water is growing. Therefore, by measuring and comparing both water temperatures, it is possible to monitor whether or not heat exchange is normally performed in the heat exchanger 12 from the temperature difference.

(Eleventh embodiment)
In an eleventh embodiment described next, a water level sensor is provided.

  FIG. 21 is an enlarged vertical sectional view of the motor unit 11 according to the eleventh embodiment of the present invention. The pump includes a water level sensor 31 installed at a position where the water level of the circulating coolant 29 can be measured. The water level sensor 31 is, for example, an electrode type water level sensor, and is preferably inserted from the upper part of the housing 8 because the length of the electrode rod can be adjusted in accordance with the prescribed required water level. In order to prevent the water level sensor 31 from losing its function due to water immersion on the pump installation floor, it is preferable to select a waterproof type when installing the water level sensor 31 below the water level where water immersion is assumed.

  In the motor 10 with the heat exchanger 12, the circulating coolant 29 circulates in the motor unit 11 in order to cool the heat generated by the motor 10. If it is normal, the circulating coolant 29 does not leak to the outside, so its water level is constant. By measuring the water level of the circulating coolant 29 circulating in the motor 10 by the water level sensor 31, leakage of the circulating coolant 29 can be monitored. For example, when the measured water level is below a predetermined value, it can be detected that the circulating cooling liquid 29 is reduced and the efficiency of heat exchange is reduced.

(Twelfth embodiment)
In a twelfth embodiment described next, an inspection window is provided.

  FIG. 22 is a vertical sectional view showing a pump according to the twelfth embodiment of the present invention. This pump is provided with a transparent inspection window 32 such as an acrylic plate having a strength capable of withstanding the internal pressure provided in the sub-flow pipe portion 4 a of the pump casing 3. The inspector visually observes the state inside the pump through the inspection window 32, particularly the state of the lower surface 18 of the heat exchanger 12. For example, when foreign matter or dirt adheres to the lower surface 18 of the heat exchanger 12, the heat exchange efficiency by the heat exchanger 12 is lowered. The inspector visually observes the state of the lower surface 18 of the heat exchanger 12 through the inspection window 32 and confirms whether or not the motor cooling is hindered by foreign matter, dirt, or the like adhering to the lower surface 18 of the heat exchanger 12. be able to.

  Although there is no restriction | limiting in particular in the position which provides the inspection window 32, For example, you may provide in the position which can visually recognize the location where a foreign material etc. collect easily, such as the subchannel pipe part 4a side vicinity of the groove | channel 14. In FIG. 22, only one inspection window 32 is shown, but several inspection windows may be provided. By providing a plurality of locations, the light can be extracted into the sub-flow channel pipe portion 4a, so that the illuminance in the sub-flow channel tube portion 4a is increased, and the visual recognition is easy.

(13th Embodiment)
A thirteenth embodiment to be described next is provided with a handhole.
FIG. 23 is a vertical sectional view showing a pump according to the thirteenth embodiment of the present invention. This pump is provided in the pump casing 3 and includes a hand hole 33 that can be opened and closed.

When the pump is normally operated, the handhole 33 is in a closed state. When it is estimated that foreign matter or dirt adheres to the lower surface 18 of the heat exchanger 12 by monitoring each temperature described above, or when they are confirmed by visual recognition from the inspection window 32 described above Or when the flow rate of the drain pipe 17 described above is estimated to block the entrance of the groove 14 (on the side of the sub-flow pipe portion 4a) due to foreign matter or the like, or the foreign matter is clogged in the groove 14. Can open the hand hole 33 and remove foreign matter, dirt, and the like from the hand hole 33.
The embodiments described above may be arbitrarily combined.

  A part or all of the flow rate sensor 21 according to the sixth embodiment, the temperature sensor 30a according to the ninth embodiment, the temperature sensors 30b and 30c according to the tenth embodiment, and the water level sensor 31 according to the eleventh embodiment are pumped. Alternatively, it may be installed in the motor unit 11 to form a so-called IOT (Internet of Things). For example, some or all of these sensors are connected to the Internet together with motor current values and pressure sensors for capturing the operating state of the pump, and the measurement results of each sensor can be monitored via the Internet. Good. Moreover, a measurement result can be continuously recorded on a server. The monitor can use trend management analysis by himself / herself or artificial intelligence technology from the recorded data, and can estimate the maintenance time or use it for preventive maintenance.

  The 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.

DESCRIPTION OF SYMBOLS 1 Suction port 2 Discharge port 3 Pump casing 4 Opening 4a Subflow pipe part 4b Bend pipe part 5 Main shaft 6 Impeller 8 Motor housing 9 Output shaft 10 Motor 11 Motor part 12 Heat exchanger 13 First flange 14 Groove 15 Second flange 16 Suction water tank 17 Drain pipe 18 Lower surface 19 of heat exchanger Partition member 20 Water flow part 21 Flow rate sensor 22 First valve 23 Second valve 24 Channel 25 Flushing pump 26 Crushing cutter 27 Fixed blade 28 Crushing means 29 Circulating coolant 30a, 30b, 30c Temperature sensor 31 Water level sensor 32 Inspection window 33 Hand hole 34 Piping flange 40 Submersible shaft joint 41 Rubber string 42 O-ring 43 Water storage tank 44 Third valve 45 Rotary blade 46 Water jacket

Claims (11)

A pump casing for guiding water from a suction port facing downward to a discharge port facing sideways, the pump casing having a sub-flow pipe section provided with a first flange defining an opening above the suction port When,
A main shaft extending substantially vertically in the pump casing;
An impeller fixed to the main shaft at a lower portion in the pump casing;
A motor housing disposed on the first flange; an output shaft coupled to the main shaft from the motor housing through the first flange; and a motor provided in the motor housing for rotating the main shaft. A motor part having
A heat exchanger provided in the vicinity of the opening;
A second flange provided in the motor housing and / or the heat exchanger and fastened to the first flange;
With
A vertical shaft pump in which water can flow out from between the first flange and the second flange.   The vertical shaft pump according to claim 1, wherein a groove through which water can flow out is provided in the first flange.   The vertical shaft pump according to claim 1 or 2, wherein a groove through which water can flow out is provided in the second flange.   The vertical shaft pump according to claim 2 or 3, wherein the upper surface of the groove is at the same level as the lower surface of the heat exchanger or higher than the lower surface of the heat exchanger.   The vertical shaft pump according to any one of claims 2 to 4, further comprising a drain pipe connected to the groove and opened downward.   The vertical shaft pump according to claim 5, wherein a flow rate sensor is provided in the drain pipe. A flow path branched from the drain pipe;
A first valve provided on the downstream side of a branch point with the flow path in the drain pipe;
A second valve provided in the flow path;
A flushing pump provided in the flow path,
The vertical shaft pump according to claim 5 or 6, wherein foreign matter accumulated in the vicinity of the groove in the drain pipe is poured into the pump casing.   The vertical shaft pump according to any one of claims 2 to 7, wherein a lower surface of the heat exchanger is inclined so as to increase in a vertical direction toward the groove. A crushing cutter that rotates with the main shaft;
The vertical shaft pump according to claim 2, further comprising a fixed blade provided in the vicinity of the groove. A partition member provided below the heat exchanger in the sub-flow channel section;
The vertical shaft pump according to any one of claims 1 to 8, wherein water can pass from the partition member to the heat exchanger side.   The vertical shaft pump according to claim 10, wherein water can pass from the partition member to the heat exchanger side on the opposite side of the groove with respect to the main shaft.

Images