JP7067443B2 - underwater pump - Google Patents

Description

The present invention relates to a submersible pump.

Conventionally, a submersible pump that cools a motor with a coolant is known (see, for example, Patent Document 1).

The above-mentioned Patent Document 1 discloses a submersible pump including a motor, a coolant circulation flow path of a coolant for cooling the motor, and a mechanical seal provided on the coolant circulation flow path. The submersible pump is configured to use the coolant of the motor as the lubricating fluid of the mechanical seal.

Japanese Patent No. 5552402

However, in the submersible pump of Patent Document 1, since the liquid flowing through the cooling liquid circulation flow path is used for both cooling and lubrication, there is a problem that the optimum liquid for each application cannot be selected. .. Further, when the liquid in the pump chamber enters the coolant circulation flow path through the mechanical seal, there is a problem that the coolant is immediately contaminated. If the coolant is contaminated, scum or the like contained in the infiltrated liquid may block the flow path and stop the circulation of the coolant, which is not preferable. That is, it is not preferable because the function of cooling the motor is hindered.

The present invention has been made to solve the above-mentioned problems, and one object of the present invention is to select an optimum liquid as each liquid for cooling a motor and lubricating a mechanical seal. It is possible to provide a submersible pump capable of suppressing contamination of the coolant.

The submersible pump according to one aspect of the present invention includes a motor including a drive shaft, a pump chamber in which an impeller driven by the motor is arranged, a suction port and a discharge port are provided, and a mechanical seal having a sliding portion. An oil chamber provided between the motor and the pump chamber, a motor cooling chamber arranged adjacent to the motor and cooling the motor with a coolant, and a motor cooling chamber arranged adjacent to the pump chamber to charge the coolant. A heat exchange chamber that exchanges heat between the coolant and the liquid in the pump chamber by flowing is provided outside the drive shaft in the radial direction with respect to the oil chamber, and the heat exchange chamber and the motor cooling chamber are communicated with each other. A first flow path for flowing a coolant from one of the heat exchange chamber and the motor cooling chamber to the other, and a first flow path provided on the outside in the radial direction with respect to the oil chamber, communicating the heat exchange chamber and the motor cooling chamber, and the first. A second flow path for flowing the cooling liquid in the direction opposite to the flow path is provided.

In the submersible pump according to one aspect of the present invention, as described above, a first flow path, a second flow path, a motor cooling room, and a heat exchange room for flowing the coolant are provided separately from the oil chamber. Since the cooling of the motor and the lubrication of the mechanical seal can be performed by separate liquids, the optimum liquid can be selected as the respective liquids for cooling the motor and lubricating the mechanical seal. Further, even when the liquid in the pump chamber infiltrates through the mechanical seal, the liquid (oil) in the oil chamber can be contaminated first, so that the contamination of the coolant can be prevented. As described above, the optimum liquid can be selected as the respective liquids for cooling the motor and for lubricating the mechanical seal, and contamination of the coolant can be suppressed. In addition, since the coolant circulation pump chamber can be arranged along the drive shaft at a position farther from the oil chamber than the oil chamber, the oil chamber should be the destination of sewage in case of inundation. Can be done. As a result, contamination of the coolant can be further suppressed.

In the submersible pump according to the above one aspect, preferably, the heat exchange chamber is provided with a watertight seal structure to the outside. With such a configuration, the seal structure can effectively prevent the infiltration of liquid or air into the heat exchange chamber from the outside of the heat exchange chamber such as the pump chamber side, the atmosphere side, and the oil chamber side. As a result, contamination of the coolant can be further suppressed.

In the submersible pump according to the above one aspect, preferably, the first flow path and the second flow path extend in the axial direction of the drive shaft along the outer periphery of the oil chamber outside the radial direction of the drive shaft of the oil chamber. ing. With this configuration, the first flow path and the second flow path can be compared with the case where the first flow path and the second flow path extend in the direction intersecting the axial direction of the drive shaft around the oil chamber. Since the length of the flow path can be shortened, the energy loss in the flow path can be reduced and the motor can be cooled efficiently.

In the submersible pump according to the above one aspect, preferably, at least one of the first flow path and the second flow path is formed so as to surround substantially the entire circumference of the oil chamber. With this configuration, the coolant can flow into the heat exchange chamber from substantially the entire circumference of the oil chamber, so that a large heat transfer area between the coolant in the heat exchange chamber and the liquid in the pump chamber can be secured. can. As a result, heat exchange between the coolant and the liquid in the pump chamber can be effectively performed.

In the submersible pump according to the above one aspect , preferably, the second flow path is arranged inside in the radial direction of the drive shaft of the first flow path, and the coolant from the heat exchange chamber is supplied by the coolant circulation impeller. The coolant is configured to flow into the coolant circulation pump chamber and the coolant flowing out of the coolant circulation pump chamber to flow into the motor cooling chamber. With this configuration, the cooling liquid cooled in the heat exchange chamber can be effectively flowed to the second flow path closer to the motor than the first flow path in the radial direction of the drive shaft. The motor can be cooled.

In the submersible pump according to the above one aspect , preferably, the second flow path is arranged inside in the radial direction of the drive shaft of the first flow path, and the coolant from the motor cooling chamber is supplied by the coolant circulation impeller. The coolant is configured to flow into the coolant circulation pump chamber and the coolant flowing out of the coolant circulation pump chamber to flow into the heat exchange chamber. With this configuration, the coolant circulation impeller allows the coolant to flow toward the heat exchange chamber side opposite to the motor (excluding the drive shaft), so the motor side is set to negative pressure. , Water intrusion into the motor can be effectively suppressed.

In the submersible pump according to the above one aspect, preferably, one first housing portion including an oil exchange hole for communicating the atmosphere and the oil chamber and provided with the oil chamber is further provided. With this configuration, it is possible to save the trouble of assembling the plurality of housing portions as compared with the case where the oil exchange holes are provided across the plurality of housing portions. In addition, the number of sealing members required to prevent oil leakage can be reduced.

In this case, preferably, the first housing portion is configured so that the oil exchange hole and the first flow path and the second flow path provided in the first housing portion do not overlap each other in a plan view. .. With such a configuration, it is possible to prevent the flow of the coolant in the first flow path and the second flow path from being obstructed by the oil exchange hole, and it is possible to prevent the structure of the first housing portion from becoming complicated. be able to.

In the submersible pump according to the above one aspect, preferably, at least one first flow path is provided, arranged outside the drive axis of the second flow path in the radial direction, and an arc surrounding the drive shaft in a plan view. It is formed in a shape. With this configuration, the shape of the first flow path can be made along the outer circumference of the motor.

In the configuration in which the heat exchange chamber is provided with a seal structure, preferably, the heat exchange chamber side is opened, the first housing portion provided with the oil chamber and the first housing portion side are opened, and the heat exchange chamber is opened. The second housing portion provided with the above, and a partition member arranged between the first housing portion and the second housing portion and partitioning the oil chamber and the heat exchange chamber are further provided, and the seal structure is the first. 1 Includes a seal member provided between the housing portion and the partition member and watertightly sealing between the oil chamber and the heat exchange chamber. With this configuration, the sealing member can be used to hermetically seal the space between the oil chamber and the heat exchange chamber, and prevent the oil from contaminating the coolant.

In the configuration in which the heat exchange chamber is provided with a seal structure, preferably, the heat exchange chamber side is opened, the first housing portion provided with the oil chamber and the first housing portion side are opened, and the heat exchange chamber is opened. The second housing portion provided with the above, and a partition member arranged between the first housing portion and the second housing portion and partitioning the oil chamber and the heat exchange chamber are further provided, and the seal structure is the first. 2 Includes an integral structure in which the housing portion and the partition member are integrally formed. With this configuration, it is possible to reduce the number of places where sealing is required and improve the watertightness of the heat exchange chamber. As a result, the device configuration can be further simplified.

In the submersible pump according to the above one aspect , preferably, a first housing portion provided with an oil chamber, a second housing portion provided with a heat exchange chamber, and a second housing portion provided with a cooling liquid circulation pump chamber are provided. A third housing portion and a fourth housing portion provided between the third housing portion and the motor are further provided, and the first flow path and the second flow path are the first housing with respect to the pump chamber. By stacking the body portion, the second housing portion, the third housing portion, and the fourth housing portion in the order of the second housing portion, the first housing portion, the third housing portion, and the fourth housing portion. It is formed. With this configuration, the first housing unit, the second housing unit, the third housing unit, and the fourth housing unit can be combined with the second housing unit, the first housing unit, the third housing unit, and the third housing unit. The pump body can be easily assembled by simply stacking the fourth housing portions in this order.

In this case, preferably, the fourth housing portion includes a motor-side first opening for communicating the first flow path with the motor cooling chamber and a motor-side second opening for communicating the second flow path with the motor cooling chamber. The first opening on the motor side and the second opening on the motor side are provided at positions deviated from each other in the circumferential direction of the drive shaft, respectively. With this configuration, the first opening on the motor side and the second opening on the motor side can be used as an opening for flowing the cooling liquid to the motor cooling chamber and an opening for flowing the cooling liquid to the heat exchange chamber.

In the configuration in which the second housing portion, the first housing portion, the third housing portion, and the fourth housing portion are stacked in this order, the fourth housing portion preferably extends along the lower surface of the motor. The second flow path extends in the radial direction of the drive shaft between the third housing portion and the fourth housing portion along the lower surface of the motor, and one end and the other end are a coolant circulation pump chamber and a cooling liquid circulation pump chamber, respectively. Includes the lower flow path of the motor connected to the motor cooling chamber. With this configuration, the motor can be cooled from below by the coolant flowing through the lower flow path of the motor.

In the configuration in which the second housing portion, the first housing portion, the third housing portion, and the fourth housing portion are stacked in this order, the second housing portion is preferably a heat exchange chamber in the axial direction of the drive shaft. The position is formed so as to overlap the position of the oil chamber in the axial direction of the drive shaft. With this configuration, the heat exchange chamber and the oil chamber do not overlap in the axial direction of the drive shaft, and the heat exchange chamber and the oil chamber are arranged along the drive shaft. The length can be shortened. That is, the device can be miniaturized in the axial direction.

In the submersible pump according to the above one aspect, preferably, the heat exchange chamber regulates the flow of the coolant flowing in from the radial outside of the drive shaft so that it flows along the drive shaft and flows out from the radial outside. Includes guide members. With this configuration, the guide member regulates the flow of the coolant so that it can flow along the drive shaft (circumferential direction of the drive shaft) during driving, and the coolant can flow along the pump chamber. The flow of coolant in the heat exchange chamber can be rectified.

In this case, preferably, the guide member has a gap at the radial inner end of the drive shaft that is part of the cooling liquid flow path, and includes a plurality of rib portions that extend radially. With this configuration, the rib portion allows the flow path of the coolant in the heat exchange chamber to have a shape including folding back, so that the flow path of the coolant in the heat exchange chamber can be lengthened and the coolant can be cooled. The heat exchange between the liquid and the liquid in the pump chamber can be performed more effectively.

In the submersible pump according to the above one aspect, preferably, a storage chamber arranged between the motor and the oil chamber and a liquid level sensor for detecting a predetermined liquid level of the liquid flowing into and stored in the storage chamber are further added. Be prepared. With this configuration, the storage chamber can prevent the liquid from rising to the motor side. In addition, the liquid level sensor can detect oil rising or inundation in the storage chamber. As a result, maintenance work can be reliably performed before the oil rises or floods occur in the motor.

In the submersible pump according to the above one aspect, the heat exchange chamber is preferably provided on the outer side in the radial direction of the pump chamber. With this configuration, it is possible to secure a large heat transfer area between the heat exchange chamber and the pump chamber by using substantially the entire circumference of the outer circumference of the pump casing, so that heat exchange can be effectively performed. In addition, heat can be effectively exchanged between the coolant in the heat exchange chamber and the fluid outside the submersible pump. Also, in the case of a vertical submersible pump, the heat exchange chamber can be arranged at a relatively low position, so that even if the water level outside the submersible pump is lower, the coolant in the heat exchange chamber and the submersible pump can be used. Heat exchange with an external fluid can be performed more effectively. Further, the length of the drive shaft is shortened as compared with the case where the heat exchange chamber and the pump chamber are arranged along the drive shaft without overlapping the heat exchange chamber and the pump chamber in the axial direction of the drive shaft. be able to. That is, the device can be miniaturized in the axial direction.

According to the present invention, as described above, it is possible to select the optimum liquid as each liquid for cooling the motor and for lubricating the mechanical seal, and it is possible to suppress contamination of the coolant. A submersible pump can be provided.

It is a schematic diagram which showed the submersible pump by 1st Embodiment of this invention. It is an exploded perspective view which showed the cross section of the housing part of the submersible pump by 1st Embodiment of this invention. It is a side view which showed the oil housing of the submersible pump by 1st Embodiment of this invention. FIG. 3 is a cross-sectional view taken along the line 1000-1000 of FIG. It is a top view which showed the cooling casing of the submersible pump by 1st Embodiment of this invention. It is a schematic diagram which showed the submersible pump by the 2nd Embodiment of this invention. It is a schematic diagram which showed the submersible pump by the 3rd Embodiment of this invention. It is a schematic diagram which showed the submersible pump by the 4th Embodiment of this invention. It is sectional drawing of the oil housing of the submersible pump by the 3rd Embodiment of this invention, and is the figure corresponding to FIG. It is a schematic diagram which showed the submersible pump by the 5th Embodiment of this invention. It is a schematic partial enlarged view which showed the submersible pump by the 6th Embodiment of this invention. It is a schematic diagram which showed the submersible pump by the 7th Embodiment of this invention. It is a plan view of the cooling casing of the submersible pump according to the 7th Embodiment of this invention, and is the figure corresponding to FIG. It is the schematic which showed the submersible pump by the 8th Embodiment of this invention. It is a plan view of the cooling casing of the submersible pump according to the eighth embodiment of the present invention, and is the figure corresponding to FIG. It is the schematic which showed the submersible pump by the 9th Embodiment of this invention. 16 is a cross-sectional view taken along the line 1100-1100 of FIG. 16 is a cross-sectional view taken along the line 1200-1200 of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[First Embodiment]
(Construction of submersible pump)
The first embodiment of the present invention will be described with reference to FIGS. 1 to 5. As shown in FIG. 1, the submersible pump 100 according to the first embodiment includes a motor 10, a head cover 11, a pump chamber 12, a pump casing 13, an impeller 14, an oil chamber 15, and a housing portion 2. A cooling liquid circulation unit 3 provided in the housing unit 2 and a sealing member 4 are provided.

The seal member 4 is provided in the heat exchange chamber 31 described later in the coolant circulation unit 3. The seal member 4 has a watertight structure with respect to the outside, and prevents the liquid from entering from the pump chamber 12 side. That is, the seal member 4 prevents the coolant from being contaminated by the infiltration of water from the pump chamber 12 side.

The submersible pump 100 is an internal cooling type pump. Specifically, the submersible pump 100 is configured to cool the motor 10 with the coolant circulated by the coolant circulation unit 3. The submersible pump 100 is configured to exchange heat between the cooling liquid and the liquid in the pump chamber 12 in the heat exchange chamber 31. That is, the submersible pump 100 is configured to cool the coolant in the heat exchange chamber 31. The coolant is, for example, water to which glycol is added.

Therefore, the submersible pump 100 can be used even in an environment where the water level of the liquid around the submersible pump 100 drops depending on the situation and the submersible pump 100 is exposed. In addition, the submersible pump 100 can be used even in an environment similar to that of a land pump that is always exposed. Further, the submersible pump 100 is a vertical pump in which the drive shaft 10a of the motor 10 extends in the vertical direction.

Here, in the following description, the axial direction of the drive shaft 10a of the motor 10 is the Z direction (vertical direction). Of the Z directions, the upper side is the Z1 direction and the lower side is the Z2 direction. Further, the radial direction of the drive shaft 10a is the A direction. Of the A directions, the direction facing the outside in the radial direction of the drive shaft 10a is the A1 direction, and the direction opposite to the A1 direction is the A2 direction.

The motor 10 is hermetically sealed so that a liquid from the outside does not enter. The motor 10 includes a drive shaft 10a, a stator 10b, a rotor 10c, and a motor frame 10d. The motor 10 is configured to rotationally drive the impeller 14 connected to the drive shaft 10a via the drive shaft 10a. Specifically, the motor 10 is an inner rotor motor in which the stator 10b is arranged on the outer side (A1 direction side) of the rotor 10c in the radial direction and is attached to the inner side of the motor frame 10d. The rotor 10c is attached to the drive shaft 10a and is configured to rotate together with the drive shaft 10a by a magnetic field from the stator 10b. The rotor 10c is configured to rotationally drive the impeller 14 via the drive shaft 10a.

The drive shaft 10a is rotatably supported by bearings 16a and 16b. The bearing 16a is supported on the Z1 direction side of the motor 10 by a head cover 11 described later in the housing portion 2. The bearing 16b is supported on the Z2 direction side of the motor 10 by a bearing cover 21 described later in the housing portion 2. From the Z1 direction side along the drive shaft 10a (Z direction), the motor 10, the cooling liquid circulation pump chamber 34, the oil chamber 15, the heat exchange chamber 31, and the pump chamber 12, which will be described later, of the coolant circulation unit 3 are located. They are arranged in order.

An impeller 14 driven by a motor 10 is arranged in the pump chamber 12. The pump chamber 12 is provided in the pump casing 13. The pump casing 13 is provided with a liquid (sewage or the like) suction port 13a and a discharge port 13b. The pump casing 13 is arranged on the lower side (Z2 direction side) of the housing portion 2.

By rotating the impeller 14, the water in the drainage region where the submersible pump 100 is arranged is sucked into the pump casing 13 (pump chamber 12) from the suction port 13a, and the sucked water is sucked into the discharge port 13b (generally A1). It is configured to send in the direction).

The oil chamber 15 is arranged between the motor 10 and the pump chamber 12 and is filled with oil. The oil chamber 15 includes a mechanical seal 15a and an electrode type sensor 15b.

The mechanical seal 15a has sliding portions on the load side (pump chamber 12 side, that is, the Z2 direction side) and the counterload side (opposite side to the pump chamber 12, that is, the Z1 direction side), respectively. The sliding portion on the load side has a function of suppressing the pressure water of the pump chamber 12 from flowing into the oil chamber 15. Further, the sliding portion on the non-load side has a function of suppressing the liquid containing oil in the oil chamber 15 from flowing into the cooling liquid circulation pump chamber 34. The sliding portion is lubricated by the oil filled in the oil chamber 15 and cooled so as not to be seized. Since the mechanical seal 15a has a slight gap formed between the fixed ring and the rotating ring constituting the mechanical seal 15a, even if it functions normally, it is pumped into the oil chamber 15 little by little. Liquid enters from the chamber 12.

The electrode type sensor 15b is configured to be able to detect the infiltration of liquid from the pump chamber 12 into the oil chamber 15. The electrode type sensor 15b is configured to detect the infiltration of liquid by energizing the oil chamber 15 with the oil housing 23 by the liquid invading the oil chamber 15.

(Structure of coolant circulation part and housing part)
As shown in FIG. 1, the coolant circulation unit 3 is configured to circulate the coolant in the pump body between the pump chamber 12 and the head cover 11 in order to cool the motor 10. The coolant circulation unit 3 is configured so that the oil in the oil chamber 15 does not get mixed in the coolant.

The coolant circulation unit 3 is provided in the motor cooling chamber 30, the heat exchange chamber 31 (the space where the coolant is cooled), the first flow path 32, the second flow path 33, and the second flow path 33. It is provided with a cooling liquid circulation pump chamber 34.

The coolant circulation unit 3 includes a coolant circulation pump chamber 34, a downstream flow path (motor lower flow path 33b described later) of the coolant circulation pump chamber 34 of the second flow path 33, a motor cooling chamber 30, and a second flow path. Coolant is circulated in the order of 1 flow path 32, the heat exchange chamber 31, and the upstream side flow path (flow path 33a described later) of the coolant circulation pump chamber 34 of the second flow path 33, and the coolant is circulated again. It is configured to be returned to the pump chamber 34.

The housing portion 2 includes a water jacket 20, a bearing cover 21, a cooling housing 22, an oil housing 23, an oil casing 24, and a cooling casing 25, one by one. The bearing cover 21 is an example of the "fourth housing portion" in the claims. The cooling housing 22 is an example of the "third housing portion" in the claims. The oil casing 24 is an example of a "partition member" within the scope of the claims. The oil housing 23 is an example of the "first housing portion" in the claims. The cooling casing 25 is an example of the "second housing portion" in the claims.

The first flow path 32 and the second flow path 33 have a bearing cover 21, a cooling housing 22, an oil housing 23, an oil casing 24, and a cooling casing 25 with respect to the pump chamber 12 (pump casing 13). , The cooling casing 25, the oil casing 24, the oil housing 23, the cooling housing 22, and the bearing cover 21 are stacked in this order from the Z2 direction side to the Z1 direction side. The housing portion 2 is provided with a sealing member (for example, an O-ring) in each portion so that the cooling liquid, the oil in the oil chamber 15, and the atmosphere and the liquid in the pump chamber 12 do not mix with each other. Has been done.

The outer diameters (sizes in the A direction) of each part (water jacket 20, bearing cover 21, cooling housing 22, oil housing 23, cooling casing 25) constituting the housing part 2 excluding the oil casing 24 are generally substantially different from each other. It is formed to be the same. The bearing cover 21 extends in the radial direction (A direction) of the drive shaft 10a along the lower surface of the motor 10 (excluding the drive shaft 10a).

The oil housing 23 is provided with an oil chamber 15 with the heat exchange chamber 31 side (Z2 direction side) open. The cooling casing 25 is open on the oil housing 23 side (Z1 direction side) and is provided with a heat exchange chamber 31. The oil casing 24 is arranged between the oil housing 23 and the cooling casing 25, and partitions the oil housing 23 and the cooling casing 25. That is, the oil casing 24 prevents the oil in the oil chamber 15 and the coolant in the heat exchange chamber 31 from mixing with each other.

The motor cooling chamber 30 is provided in the water jacket 20 and is arranged adjacent to the motor 10 so as to cover the motor 10 from the outer peripheral side (A1 direction side). That is, the motor cooling chamber 30 is a cylindrical space portion.

The motor cooling chamber 30 includes a partition wall portion 30a, an inner cooling chamber 30b, and an outer cooling chamber 30c.

The partition wall portion 30a has a cylindrical shape extending upward from the lower end (Z2 direction side end portion), and is a plate-shaped wall that divides the motor cooling chamber 30 into an inner cooling chamber 30b and an outer cooling chamber 30c. The partition wall portion 30a has a gap at the upper end (Z1 direction side end portion). The inner cooling chamber 30b is arranged inside the partition wall portion 30a (on the A2 direction side). The outer cooling chamber 30c is arranged on the outside (A1 direction side) of the partition wall portion 30a. The inner cooling chamber 30b and the outer cooling chamber 30c communicate with each other through the gap at the upper end of the partition wall portion 30a. The upper end of the partition wall portion 30a is located on the Z1 direction side of the stator 10b and the rotor 10c of the motor 10.

The inner cooling chamber 30b communicates with the second flow path 33 (the lower flow path 33b of the motor described later) (the inflow port 21a described later provided on the bearing cover 21) at the lower end (the end portion on the Z2 direction side). Therefore, the inner cooling chamber 30b is configured to be able to effectively cool the motor 10 by flowing the cooling liquid from the heat exchange chamber 31 along the motor 10.

The outer cooling chamber 30c communicates with the first flow path 32 (outlet 21b described later provided in the bearing cover 21) at the lower end. Therefore, the outer cooling chamber 30c is configured to be able to be effectively cooled by the liquid surrounding the submersible pump 100 or the atmosphere before sending the heated coolant from the motor 10 to the heat exchange chamber 31.

The bearing cover 21 arranged adjacent to the water jacket 20 on the Z2 direction side is provided with a plurality (three) inlets 21a and a plurality (three) outlets 21b. The inflow port 21a is an example of the "first opening on the motor side" in the claims. The outlet 21b is an example of the "second opening on the motor side" in the claims.

The inflow port 21a communicates the second flow path 33 with the motor cooling chamber 30 (inner cooling chamber 30b) so that the cooling liquid flows from the second flow path 33 into the motor cooling chamber 30 (inner cooling chamber 30b). It is configured. The outlet 21b communicates the first flow path 32 with the motor cooling chamber 30 (outer cooling chamber 30c) so that the cooling liquid flows out from the motor cooling chamber 30 (outer cooling chamber 30c) to the first flow path 32. It is configured.

As shown in FIG. 2, the inflow port 21a and the outflow port 21b have an arc shape and are arranged at positions displaced from each other in the A direction. That is, the inflow port 21a is arranged on the A2 direction side with respect to the outflow port 21b. The plurality of inlets 21a and the plurality of outlets 21b are arranged alternately in the circumferential direction of the drive shaft 10a (see FIG. 1) at substantially equal angular intervals in a state of being displaced from each other in the A direction. That is, the motor cooling chamber 30 (see FIG. 1) makes the motor 10 (see FIG. 1) uneven by the cooling liquids flowing in and out from the plurality of inlets 21a and the plurality of outlets 21b in the circumferential direction of the drive shaft 10a. It is configured to cool without. Note that FIG. 2 shows only one side configuration of the vertical cross-sectional shape of the coolant circulation portion 3 and the housing portion 2, but the other side configuration of the vertical cross-sectional shape (not shown) has the same shape as the one side configuration ( It has a shape that is symmetrical with respect to the cross section).

The heat exchange chamber 31 is provided in the cooling casing 25. The heat exchange chamber 31 is arranged adjacent to the pump chamber 12 on the Z1 direction side. The heat exchange chamber 31 is arranged adjacent to the oil chamber 15 on the Z2 direction side. The heat exchange chamber 31 is configured to exchange heat between the coolant and the liquid in the pump chamber 12 by flowing the coolant.

As shown in FIGS. 4 and 5, the oil housing 23 is provided with a plurality (three) inlets 23a and a plurality (three) outlets 23b.

The inflow port 23a is configured so that the first flow path 32 communicates with the heat exchange chamber 31 and the cooling liquid flows from the first flow path 32 into the heat exchange chamber 31 (see FIG. 1). The outlet 23b is configured to allow the second flow path 33 to communicate with the heat exchange chamber 31 so that the cooling liquid flows out from the heat exchange chamber 31 to the second flow path 33.

The inflow port 23a and the outflow port 23b have an arc shape and are arranged at positions corresponding to each other in the A direction without being displaced from each other in the A direction. The inflow port 23a and the outflow port 23b are arranged near the outer end portion of the heat exchange chamber 31 in the A1 direction. The plurality of inlets 23a and the plurality of outlets 23b are arranged alternately in the circumferential direction of the drive shaft 10a at substantially equal angular intervals.

As shown in FIGS. 2 and 5, the heat exchange chamber 31 includes a plurality of rib portions 31a.

The plurality of rib portions 31a regulate the flow of the coolant flowing in from the outer inflow port 23a in the radial direction (A direction) and flow along the drive shaft 10a (circumferential direction of the drive shaft 10a), and also in the radial direction. It is configured to flow out from the outer outlet 23b.

Specifically, the plurality of rib portions 31a have a gap that becomes a part of the flow path in the heat exchange chamber 31 of the coolant at the inner end portion in the radial direction, and extend radially in the radial direction. That is, the plurality of rib portions 31a divide the heat exchange chamber 31 into a plurality of spaces arranged in the circumferential direction so as to have a fan shape in a plan view. As a result, the coolant flowing into the heat exchange chamber 31 from the inflow port 23a (first flow path 32) flows in the fan-shaped space toward the inside in the radial direction (A2 direction side) and inside the rib portion 31a. It passes through the gap at the end, flows into another fan-shaped space adjacent to the end, flows outward in the radial direction (A1 direction), and flows out from the outlet 23b to the second flow path 33. The plurality of rib portions 31a can efficiently circulate the coolant by rectifying (regulating) the flow of the coolant in the heat exchange chamber 31. As a result, the heat exchange chamber 31 can effectively cool the cooling liquid.

As shown in FIG. 2, a plurality (three) of the first flow paths 32 are provided outside the radial direction (A direction) of the drive shaft 10a (see FIG. 1) with respect to the oil chamber 15. The first flow path 32 communicates the heat exchange chamber 31 and the motor cooling chamber 30 (see FIG. 1). Specifically, in the first flow path 32, one end (Z2 direction side end) is communicated with the heat exchange chamber 31 via the inflow port 23a, and the other end (Z1 direction side end) is communicated with the outflow port 21b. It communicates with the motor cooling chamber 30. As a result, the first flow path 32 is configured to allow the coolant to flow from the motor cooling chamber 30 to the heat exchange chamber 31.

The first flow path 32 extends in the axial direction (Z direction) of the drive shaft 10a along the outer periphery of the oil chamber 15 outside the radial direction of the oil chamber 15. The first flow path 32 is provided so as to straddle the bearing cover 21, the cooling housing 22, and the oil housing 23. The first flow path 32 extends linearly along the axial direction (Z direction) of the drive shaft 10a.

Therefore, although not shown, the first flow path 32, the outflow port 21b, and the inflow port 23a are arranged at positions corresponding to each other in a plan view. The plurality of first flow paths 32 are arranged near the outer ends of the bearing cover 21, the cooling housing 22, and the oil housing 23 in the A1 direction, respectively, and at substantially equal angular intervals in the circumferential direction of the drive shaft 10a. They are arranged side by side.

A plurality (three) of the second flow paths 33 are provided outside the drive shaft 10a in the radial direction (A direction) with respect to the oil chamber 15 (see FIG. 4). The second flow path 33 is arranged inside the first flow path 32 in the radial direction (A direction). The second flow path 33 communicates the heat exchange chamber 31 and the motor cooling chamber 30. Specifically, in the second flow path 33, one end (Z2 direction side end) is communicated with the heat exchange chamber 31 via the outflow port 23b, and the other end (Z1 direction side end) is communicated with the inflow port 21a. It communicates with the motor cooling chamber 30. As a result, the second flow path 33 is configured to flow the coolant in the direction opposite to that of the first flow path 32 (from the heat exchange chamber 31 to the motor cooling chamber 30).

Similar to the first flow path 32, the second flow path 33 is located outside the oil chamber 15 in the radial direction (A1 direction side) in the axial direction (Z direction) of the drive shaft 10a along the outer circumference of the oil chamber 15. It is extending.

In the second flow path 33, a coolant circulation pump chamber 34 in which a coolant circulation impeller 34a for generating a flow of the coolant in the coolant circulation section 3 is arranged is provided in the middle of the flow path.

The coolant circulation impeller 34a is attached to the drive shaft 10a of the motor 10 (see FIG. 1), and is configured to be driven (rotated) by the motor 10. The coolant circulation impeller 34a is configured to generate a flow in the Z1 direction along the drive shaft 10a by driving. The cooling liquid circulation pump chamber 34 (cooling liquid circulation impeller 34a) is arranged between the motor 10 (excluding the drive shaft 10a) and the oil chamber 15. The coolant circulation impeller 34a is an axial flow type impeller that allows the coolant to flow in and out along the axial direction (Z direction) of the drive shaft 10a.

As shown in FIG. 1, the second flow path 33 includes a flow path 33a provided on the upstream side of the coolant circulation pump chamber 34 and a motor lower flow path provided on the downstream side of the coolant circulation pump chamber 34. 33b and is included.

The second flow path 33 sends the cooling liquid from the heat exchange chamber 31 to the motor cooling chamber 30 by flowing the cooling liquid in the order of the flow path 33a, the cooling liquid circulation pump chamber 34, and the motor lower flow path 33b. It is configured.

The flow path 33a has a first portion 133a extending in the axial direction (Z direction) of the drive shaft 10a, and a second portion extending inward in the radial direction (A2 direction side) of the drive shaft 10a from the end portion of the first portion 133a in the Z1 direction. It has two portions 133b. The first portion 133a is provided in the oil housing 23 in the shape of a through hole. The second portion 133b is provided between the oil housing 23 and the cooling housing 22.

The lower flow path 33b of the motor extends along the lower surface of the motor 10 (the portion excluding the drive shaft 10a) to the outside (A1 direction side) of the drive shaft 10a in the radial direction. The motor lower flow path 33b is provided between the bearing cover 21 and the cooling housing 22. One end on the upstream side of the lower flow path 33b of the motor is connected to the cooling liquid circulation pump chamber 34. The other end of the lower flow path 33b on the downstream side of the motor is connected to the motor cooling chamber 30 (inner cooling chamber 30b).

The second flow path 33 causes the cooling liquid from the heat exchange chamber 31 to flow inward (A2 direction side) in the radial direction of the drive shaft 10a along the oil chamber 15 (upper part of the oil chamber 15) by the second portion 133b. It is configured to flow into the coolant circulation pump chamber 34. Further, the second flow path 33 drives the coolant flowing out of the coolant circulation pump chamber 34 by the coolant circulation impeller 34a along the lower surface of the motor 10 (the portion excluding the drive shaft 10a). It is configured to flow to the outside (A1 direction side) in the radial direction of the shaft 10a.

As a result, the coolant flows into the motor cooling chamber 30. That is, the second flow path 33 is configured to flow the coolant in the opposite directions in the radial direction (A direction) on the upstream side and the downstream side of the coolant circulation impeller 34a.

(Construction of oil change hole)
As shown in FIGS. 3 and 4, the oil housing 23 includes an oil change hole 23c for changing oil.

The oil exchange hole 23c communicates the atmosphere (outside the submersible pump 100) with the oil chamber 15. Specifically, in the oil housing 23, the oil exchange hole 23c and the first flow path 32 and the second flow path 33 provided in the oil housing 23 do not overlap each other in a plan view (viewed from the Z direction). It is configured. The oil change hole 23c extends in a direction (A direction) orthogonal to the axial direction of the drive shaft 10a. The oil change hole 23c is arranged at a substantially intermediate position of the oil housing 23 in the Z direction. One oil change hole 23c is provided on each side of the drive shaft 10a with the drive shaft 10a interposed therebetween.

(Structure of seal member)
As shown in FIGS. 1 and 2, the oil casing 24 includes a cylindrical protrusion 24a that projects in the Z2 direction along the drive shaft 10a (see FIG. 1). The convex portion 24a is formed with an annular groove portion 24b that is recessed inward in the radial direction (on the A2 direction side) and surrounds the circumference of the drive shaft 10a. A seal member 4 is attached to the groove portion 24b. A heat exchange chamber 31 (cooling liquid) is arranged on one side of the seal member 4, and a pump chamber 12 (liquid such as sewage) is arranged on the other side of the seal member 4. The seal member 4 is composed of, for example, an O-ring.

The cooling casing 25 includes an annular recess 25a that surrounds the periphery of the drive shaft 10a that engages the convex portion 24a of the oil casing 24 from the Z2 direction side. The seal member 4 is watertightly sealed between the pump chamber 12 and the heat exchange chamber 31 by coming into contact with the inner surface of the convex portion 24a in a state of being attached to the groove portion 24b.

Since the seal member 4 is provided between the cooling casing 25 and the oil casing 24, which are stationary with each other, the seal member 4 is different from the mechanical seal 15a provided on the drive shaft 10a that is driven to rotate, and therefore has heat. It is possible to substantially reliably prevent the liquid from entering the exchange chamber 31 from the pump chamber 12.

Further, a seal member 4a is provided between the oil housing 23 and the oil casing 24. The seal member 4a is watertightly sealed between the oil chamber 15 and the heat exchange chamber 31. As a result, the seal member 4a prevents the oil in the oil chamber 15 from entering the heat exchange chamber 31. The seal member 4a is composed of, for example, an O-ring. The seal member 4a is an example of a "seal structure" within the scope of the claims.

Further, a sealing member 4b is provided between the oil housing 23 and the cooling casing 25. The seal member 4b is watertightly sealed between the atmosphere and the heat exchange chamber 31. The seal member 4b is composed of, for example, an O-ring. The seal member 4b is an example of a "seal structure" within the scope of the claims.

Further, it is also possible to provide an oil seal (not shown) along the lower surface of the drive shaft 10a and the cooling casing 25 in the Z2 direction at the top of the pump chamber 12 on the Z1 direction side. The oil seal can suppress the rise of the liquid from the pump chamber 12 toward the Z1 direction.

(Effect of the first embodiment)
The effect of the first embodiment will be described.

In the first embodiment, as described above, the first flow path 32, the second flow path 33, the motor cooling room 30, and the heat exchange room 31 for flowing the coolant are provided separately from the oil chamber 15. Since the cooling of the motor 10 and the lubrication of the mechanical seal 15a can be performed by separate liquids, the optimum liquid can be selected as the respective liquids for cooling the motor 10 and lubricating the mechanical seal 15a. .. Further, even when the liquid in the pump chamber 12 infiltrates through the mechanical seal 15a, the liquid (oil) in the oil chamber 15 can be contaminated first, so that the contamination of the coolant can be prevented. As described above, the optimum liquid can be selected as the respective liquids for cooling the motor 10 and for lubricating the mechanical seal 15a, and contamination of the cooling liquid can be suppressed.

In the first embodiment, as described above, the heat exchange chamber 31 is provided with a watertight seal structure (seal members 4, 4a, 4b) to the outside. As a result, the seal structure (seal members 4, 4a, 4b) effectively infiltrates the heat exchange chamber 31 from the outside of the heat exchange chamber 31, such as the pump chamber 12 side, the atmosphere side, and the oil chamber 15 side. Can be prevented. As a result, contamination of the coolant can be further suppressed.

In the first embodiment, as described above, the coolant circulation impeller 34a for the coolant driven by the motor 10 is arranged, and the cooling provided in the second flow path 33 between the motor 10 and the oil chamber 15 is provided. A liquid circulation pump chamber 34 is further provided. As a result, the cooling liquid circulation pump chamber 34 can be arranged at a position farther than the oil chamber 15 with respect to the pump chamber 12 along the drive shaft 10a, so that the infiltration destination of sewage should be inundated. It can be an oil chamber 15. As a result, contamination of the coolant can be further suppressed.

In the first embodiment, as described above, the first flow path 32 and the second flow path 33 are the drive shaft 10a along the outer periphery of the oil chamber 15 outside the drive shaft 10a of the oil chamber 15 in the radial direction. Extends in the axial direction of. As a result, the first flow path 32 and the second flow path 32 are compared with the case where the first flow path 32 and the second flow path 33 extend in the direction intersecting the axial direction of the drive shaft 10a around the oil chamber 15. Since the length of the flow path with the 33 can be shortened, the loss of energy in the flow path can be reduced and the motor 10 can be cooled efficiently.

In the first embodiment, as described above, the second flow path 33 is arranged inside the drive shaft 10a of the first flow path 32 in the radial direction, and is provided from the heat exchange chamber 31 by the coolant circulation impeller 34a. The coolant is made to flow into the cooling liquid circulation pump chamber 34, and the coolant flowing out from the coolant circulation pump chamber 34 is configured to flow into the motor cooling chamber 30. As a result, the cooling liquid cooled in the heat exchange chamber 31 can flow to the second flow path 33, which is closer to the motor 10 than the first flow path 32, in the radial direction of the drive shaft 10a, which is effective. The motor 10 can be cooled.

In the first embodiment, as described above, one oil housing 23 including an oil exchange hole 23c communicating the atmosphere and the oil chamber 15 and provided with the oil chamber 15 is further provided. As a result, it is possible to save the trouble of assembling the plurality of housing portions as compared with the case where the oil exchange holes are provided across the plurality of housing portions. In addition, the number of sealing members required to prevent oil leakage can be reduced.

In the first embodiment, as described above, in the oil housing 23, the oil exchange hole 23c and the first flow path 32 and the second flow path 33 provided in the oil housing 23 do not overlap each other in a plan view. It is configured. As a result, it is possible to prevent the flow of the coolant in the first flow path 32 and the second flow path 33 from being obstructed by the oil exchange hole 23c, and it is possible to prevent the structure of the oil housing 23 from becoming complicated. ..

In the first embodiment, as described above, at least one first flow path 32 is provided, arranged outside the drive shaft 10a of the second flow path 33 in the radial direction, and around the drive shaft 10a in a plan view. It is formed in an arc shape surrounding. As a result, the shape of the first flow path 32 can be changed to a shape along the outer circumference of the motor 10.

In the first embodiment, as described above, the oil housing 23 in which the heat exchange chamber 31 side is opened and the oil chamber 15 is provided, and the cooling casing 25 in which the oil housing 23 side is opened and the heat exchange chamber 31 is provided. Further, an oil casing 24 arranged between the oil housing 23 and the cooling casing 25 and partitioning the oil chamber 15 and the heat exchange chamber 31 is further provided, and a seal structure is provided between the oil casing 24 and the oil housing 23. It includes a sealing member 4a that watertightly seals between the oil chamber 15 and the heat exchange chamber 31. As a result, the sealing member 4a can watertightly seal the space between the oil chamber 15 and the heat exchange chamber 31 to prevent the oil from contaminating the coolant.

In the first embodiment, as described above, the oil housing 23 provided with the oil chamber 15, the cooling casing 25 provided with the heat exchange chamber 31, and the cooling housing 22 provided with the coolant circulation pump chamber 34. Further, a bearing cover 21 provided between the cooling housing 22 and the motor 10 is further provided, and the first flow path 32 and the second flow path 33 have the oil housing 23 and the cooling casing 25 with respect to the pump chamber 12. , The cooling housing 22 and the bearing cover 21 are formed by stacking the cooling casing 25, the oil housing 23 to which the oil casing 24 is attached, the cooling housing 22 and the bearing cover 21 in this order. As a result, the pump body can be easily assembled by simply stacking the oil housing 23, the cooling casing 25, the cooling housing 22 and the bearing cover 21 in the order of the cooling casing 25, the oil housing 23, the cooling housing 22 and the bearing cover 21. ..

In the first embodiment, as described above, the bearing cover 21 has an inflow port 21a in which the second flow path 33 communicates with the motor cooling chamber 30 and an outflow port 21b in which the first flow path 32 communicates with the motor cooling chamber 30. The inflow port 21a and the outflow port 21b are provided at positions deviated from each other in the circumferential direction of the drive shaft 10a, respectively. As a result, the inflow port 21a and the outflow port 21b can be used as an opening for flowing the cooling liquid to the motor cooling chamber 30 and an opening for flowing the cooling liquid to the heat exchange chamber 31.

In the first embodiment, as described above, the bearing cover 21 extends along the lower surface of the motor 10, and the second flow path 33 is between the cooling housing 22 and the bearing cover 21 and the lower surface of the motor 10. Along with extending in the radial direction of the drive shaft 10a, one end and the other end include a motor lower flow path 33b connected to a coolant circulation pump chamber 34 and a motor cooling chamber 30, respectively. As a result, the motor 10 can be cooled from the lower side by the coolant flowing through the lower flow path 33b of the motor.

In the first embodiment, as described above, the heat exchange chamber 31 regulates the flow of the cooling liquid flowing from the outside in the radial direction of the drive shaft 10a and flows along the drive shaft 10a, and also flows from the outside in the radial direction. The rib portion 31a to be discharged is included. The rib portion 31a regulates the flow of the coolant so that it can flow along the drive shaft 10a (circumferential direction of the drive shaft 10a) during driving, and the coolant can flow along the pump chamber 12, so that the heat exchange chamber can be used. The flow of the coolant in 31 can be rectified.

In the first embodiment, as described above, a plurality of rib portions 31a having a gap that becomes a part of the flow path of the coolant are provided at the inner end portion in the radial direction of the drive shaft 10a, and a plurality of rib portions 31a extending radially in the radial direction are provided. .. Since the rib portion 31a allows the flow path of the coolant in the heat exchange chamber 31 to have a shape including folding, the flow path of the coolant in the heat exchange chamber 31 is lengthened, and the flow path of the coolant and the pump chamber 12 is extended. The heat exchange with the liquid can be performed more effectively.

[Second Embodiment]
Next, a second embodiment will be described with reference to FIG. In the second embodiment, in addition to the configuration of the first embodiment, an example further including a storage chamber 51 arranged between the coolant circulation pump chamber 34 and the oil chamber 15 will be described. The same configuration as that of the first embodiment is illustrated with the same reference numerals as those of the first embodiment, and the description thereof will be omitted.

As shown in FIG. 6, the submersible pump 200 according to the second embodiment includes a storage chamber 51 and a liquid level sensor 52 provided in the storage chamber 51.

The storage chamber 51 is arranged between the motor 10 (excluding the drive shaft 10a) and the oil chamber 15. Specifically, the storage chamber 51 is arranged between the cooling liquid circulation pump chamber 34 and the oil chamber 15. The submersible pump 200 includes a lid member 53 attached to the oil housing 23 from above in order to form the storage chamber 51.

The liquid level sensor 52 is a float type sensor, and is configured to detect a predetermined liquid level of the liquid (oil and the liquid from the pump chamber 12) that has flowed into and stored in the storage chamber 51. A second portion 133b of the flow path 33a of the second flow path 33 is adjacently arranged on the Z1 direction side of the storage chamber 51.

The submersible pump 200 is configured to be capable of stopping the motor 10 and notifying the user when the predetermined liquid level of the storage chamber 51 is detected by the liquid level sensor 52. As a result, the submersible pump 200 can suppress the mixing of other liquids with the coolant of the coolant circulation unit 3.

The other configurations of the second embodiment are the same as those of the first embodiment.

(Effect of the second embodiment)
The effect of the second embodiment will be described.

In the second embodiment, as described above, the storage chamber 51 arranged between the motor 10 and the oil chamber 15 and the liquid level sensor that detects the predetermined liquid level of the liquid flowing into and stored in the storage chamber 51. 52 is further provided. As a result, the storage chamber 51 can prevent the liquid from rising to the motor 10 side. Further, the liquid level sensor 52 can detect oil rising or inundation in the storage chamber 51. As a result, maintenance work can be reliably performed before the oil rises or water infiltrates into the motor 10. Further, by providing the liquid level sensor 52 on the upper side of the oil chamber 15, it is possible to detect not only the infiltration of water from the pump chamber 12 into the oil chamber 15 but also the oil rising from the oil chamber 15 to the upper portion at an early stage.

The other effects of the second embodiment are the same as those of the first embodiment.

[Third Embodiment]
Next, a third embodiment will be described with reference to FIG. 7. In the third embodiment, unlike the configuration of the second embodiment, an example including a storage chamber 351 arranged between the coolant circulation pump chamber 34 and the motor 10 (excluding the drive shaft 10a) will be described. .. The same configuration as that of the second embodiment is illustrated with the same reference numerals as those of the second embodiment, and the description thereof will be omitted.

As shown in FIG. 7, the submersible pump 300 according to the third embodiment includes a storage chamber 351 and a liquid level sensor 352 provided in the storage chamber 351.

The storage chamber 351 is arranged between the motor 10 (excluding the drive shaft 10a) and the oil chamber 15. Specifically, the storage chamber 351 is arranged between the motor 10 (excluding the drive shaft 10a) and the coolant circulation pump chamber 34. The submersible pump 300 includes a lid member 353 attached from below to the bearing cover 21 to form the reservoir 351.

The liquid level sensor 352 is a float type sensor, and is configured to detect a predetermined liquid level of the liquid (cooling liquid, oil, and liquid from the pump chamber 12) that has flowed into and stored in the storage chamber 351. There is. On the Z2 direction side of the storage chamber 351, the motor lower flow path 33b of the second flow path 33 is adjacently arranged.

The submersible pump 300 is configured to be capable of stopping the motor 10 and notifying the user when the predetermined liquid level of the storage chamber 351 is detected by the liquid level sensor 352. As a result, the submersible pump 300 can prevent the liquid from entering the motor 10 (inside the motor frame 10d).

The other configurations of the third embodiment are the same as those of the second embodiment.

(Effect of the third embodiment)
The effect of the third embodiment will be described.

In the third embodiment, as described above, the storage chamber 351 and the liquid level sensor 352 are provided directly under the motor 10 (excluding the drive shaft 10a). As a result, it is possible to detect the most important oil rise or inundation in the motor 10 immediately before.

The other effects of the third embodiment are the same as those of the second embodiment.

[Fourth Embodiment]
Next, a fourth embodiment will be described with reference to FIGS. 8 and 9. In the fourth embodiment, unlike the first embodiment in which a plurality of first flow paths 32 are provided, an example in which one first flow path 432 is provided will be described. The same configuration as that of the first embodiment is illustrated with the same reference numerals as those of the first embodiment, and the description thereof will be omitted.

As shown in FIG. 8, the submersible pump 400 according to the fourth embodiment includes one first flow path 432, one second flow path 433, a heat exchange chamber 431, and an oil housing 423.

The first flow path 432 is arranged on the outer side (A1 direction side) of the drive shaft 10a of the second flow path 433 in the radial direction. The first flow path 432 is formed in an arc shape (C-shape) surrounding the drive shaft 10a in a plan view (viewed from the Z1 direction side) (see FIG. 9). An oil change hole 23c is arranged in the C-shaped open portion of the first flow path 432. The second flow path 433 is also formed in an arc shape (C-shape) similar to that of the first flow path 432 in a plan view (viewed from the Z1 direction side) (see FIG. 9). Therefore, the first flow path 432 and the second flow path 433 are formed so as to surround substantially the entire circumference of the oil chamber 15.

The heat exchange chamber 431 includes a flat plate-shaped horizontal rib portion 431a extending in a direction (horizontal direction) intersecting the axial direction (Z direction) of the drive shaft 10a. The horizontal rib portion 431a has a gap at the end portion on the A2 direction side, and forms a flow path of the cooling liquid that is folded back in the vertical direction at the end portion on the A2 direction side. The horizontal rib portion 431a is an example of a "guide member" within the scope of the claims.

The other configurations of the fourth embodiment are the same as those of the first embodiment.

(Effect of Fourth Embodiment)
The effect of the fourth embodiment will be described.

In the fourth embodiment, as described above, the first flow path 432 and the second flow path 433 are formed so as to surround substantially the entire circumference of the oil chamber 15. As a result, the coolant can flow into the heat exchange chamber 431 from substantially the entire circumference of the oil chamber 15, so that a large heat transfer area between the coolant in the heat exchange chamber 431 and the liquid in the pump chamber 12 can be secured. can. As a result, heat exchange between the coolant and the liquid in the pump chamber 12 can be effectively performed.

In the fourth embodiment, as described above, at least one first flow path 432 is provided, arranged outside the drive shaft 10a of the second flow path 433 in the radial direction, and around the drive shaft 10a in a plan view. It is formed in an arc shape (C-shaped) surrounding the. This makes it possible to simplify the configuration of the first flow path 432.

The other effects of the fourth embodiment are the same as those of the first embodiment.

[Fifth Embodiment]
Next, a fifth embodiment will be described with reference to FIG. The fifth embodiment is different from the first embodiment in which the oil casing 24 and the cooling casing 25 are separately provided (that is, the oil casing 24 and the cooling casing 25 are separated), and the oil casing 24 is provided. An example in which the cooling casing 25 and the cooling casing 25 are integrally formed will be described. The same configuration as that of the first embodiment is illustrated with the same reference numerals as those of the first embodiment, and the description thereof will be omitted.

As shown in FIG. 10, the submersible pump 500 according to the fifth embodiment includes a casing 525 configured by integrally forming the oil casing 24 (portion) and the cooling casing 25 (portion). .. The casing 525 is an example of the "seal structure" and the "integral structure" in the claims.

The submersible pump 500 has no gap between the oil casing 24 (portion) and the cooling casing 25 (portion), and unlike the submersible pump 100 of the first embodiment, the submersible pump 500 is not provided with the sealing member 4.

The other configurations of the fifth embodiment are the same as those of the first embodiment.

(Effect of the fifth embodiment)
The effect of the fifth embodiment will be described.

In the fifth embodiment, as described above, the oil housing 23 in which the heat exchange chamber 31 side is opened and the oil chamber 15 is provided, and the cooling casing 25 in which the oil housing 23 side is opened and the heat exchange chamber 31 is provided. Further, an oil casing 24 which is arranged between the oil housing 23 and the cooling casing 25 and partitions the oil chamber 15 and the heat exchange chamber 31 is further provided, and the sealing structure is such that the cooling casing 25 and the oil casing 24 are integrally provided. Includes the casing 525 formed. This makes it possible to reduce the number of places where sealing is required and improve the watertightness of the heat exchange chamber 31. As a result, the device configuration can be further simplified.

The other effects of the fifth embodiment are the same as those of the first embodiment.

[Sixth Embodiment]
Next, the sixth embodiment will be described with reference to FIG. The sixth embodiment describes an example in which the cooling liquid is flowed in the direction opposite to that of the first embodiment. The same configuration as that of the first embodiment is illustrated with the same reference numerals as those of the first embodiment, and the description thereof will be omitted.

As shown in FIG. 11, the submersible pump 600 according to the sixth embodiment includes a coolant circulation impeller 634a.

The coolant circulation impeller 634a is attached to the drive shaft 10a of the motor 10 and is configured to be driven (rotated) by the motor 10. The coolant circulation impeller 634a has the same shape as the coolant circulation impeller 34a (see FIG. 1) of the first embodiment, and is arranged at the same position, but the coolant circulation impeller 34a Is attached to the drive shaft 10a upside down. Therefore, the coolant circulation impeller 634a is configured to generate a flow in the Z2 direction (oil chamber 15) along the drive shaft 10a by driving.

The other configurations of the sixth embodiment are the same as those of the first embodiment.

(Effect of the sixth embodiment)
The effect of the sixth embodiment will be described.

In the sixth embodiment, as described above, the second flow path 33 is arranged inside the drive shaft 10a of the first flow path 32 in the radial direction, and is provided from the motor cooling chamber 30 by the coolant circulation impeller 634a. The coolant is configured to flow into the coolant circulation pump chamber 34, and the coolant flowing out of the coolant circulation pump chamber 34 is configured to flow into the heat exchange chamber 31. As a result, the coolant circulation impeller 634a allows the coolant to flow toward the heat exchange chamber 31 side opposite to the motor 10 (excluding the drive shaft 10a), so that the motor 10 side has a negative pressure. Therefore, water intrusion into the motor 10 can be effectively suppressed.

The other effects of the sixth embodiment are the same as those of the first embodiment.

[7th Embodiment]
Next, a seventh embodiment will be described with reference to FIGS. 12 and 13. The seventh embodiment is different from the first embodiment in which the oil chamber 15 and the heat exchange chamber 31 are arranged so as to be arranged in the axial direction (Z direction) of the drive shaft 10a, and the oil chamber 15 and the heat exchange chamber 731 are provided. An example of arranging the drive shafts 10a so as to be aligned in the radial direction (A direction) will be described. The same configuration as that of the first embodiment is illustrated with the same reference numerals as those of the first embodiment, and the description thereof will be omitted.

As shown in FIG. 12, the submersible pump 700 according to the seventh embodiment includes a cooling casing 725 and a heat exchange chamber 731.

The cooling casing 725 has a circular opening 725a inside (A2 direction side) in the radial direction of the drive shaft 10a, and the oil casing 24 is fitted in the opening. Therefore, the heat exchange chamber 731 is arranged on the outer side (A1 direction side) of the drive shaft 10a in the radial direction. The cooling casing 725 is formed so that the position of the heat exchange chamber 731 in the axial direction (Z direction) of the drive shaft 10a overlaps with the position of the oil chamber 15 in the axial direction of the drive shaft 10a. That is, the heat exchange chamber 731 and the oil chamber 15 are arranged side by side.

The other configurations of the seventh embodiment are the same as those of the first embodiment.

(Effect of the 7th embodiment)
The effect of the seventh embodiment will be described.

In the seventh embodiment, as described above, the cooling casing 725 is formed so that the position of the heat exchange chamber 731 in the axial direction overlaps with the position of the oil chamber 15 in the axial direction. As a result, the heat exchange chamber 731 and the oil chamber 15 do not overlap in the axial direction of the drive shaft 10a, and the heat exchange chamber 731 and the oil chamber 15 are driven as compared with the case where they are arranged along the drive shaft 10a. The length of the shaft 10a can be shortened. That is, the device can be miniaturized in the axial direction.

The other effects of the seventh embodiment are the same as those of the first embodiment.

[Eighth Embodiment]
Next, the eighth embodiment will be described with reference to FIGS. 14 and 15. The eighth embodiment is different from the seventh embodiment, and like the fourth embodiment, an example in which one first flow path 832 is provided will be described. The same configuration as that of the seventh embodiment is illustrated with the same reference numerals as those of the seventh embodiment, and the description thereof will be omitted.

As shown in FIG. 14, the submersible pump 800 according to the eighth embodiment includes one first flow path 832, a heat exchange chamber 831, and a cooling casing 825.

The first flow path 832 is arranged on the outer side (A1 direction side) of the drive shaft 10a of the second flow path 833 in the radial direction. The first flow path 832 is formed in an arc shape (C-shape) surrounding the drive shaft 10a in a plan view (viewed from the Z1 direction side) (see FIG. 9). An oil change hole 23c (see FIG. 9) is arranged in the C-shaped open portion of the first flow path 832.

The heat exchange chamber 831 includes a flat plate-shaped horizontal rib portion 831a extending in a direction (horizontal direction) intersecting the axial direction (Z direction) of the drive shaft 10a. The horizontal rib portion 831a has a gap at the end portion on the A2 direction side, and forms a flow path of the cooling liquid that is folded back in the vertical direction at the end portion on the A2 direction side. The horizontal rib portion 831a is an example of a "guide member" within the scope of the claims.

As shown in FIG. 15, a plurality (6) openings 825a arranged in the circumferential direction of the drive shaft 10a and connected to the first flow path 832 are provided on the upper portion of the cooling casing 825. Further, by combining the cooling casing 825 and the oil casing 24, the second flow is arranged inside the opening 825a in the radial direction (on the A2 direction side) and above the cooling casing 825 in the circumferential direction of the drive shaft 10a. A plurality (six) openings 826 connected to the road 833 are formed. Further, in the middle of the flow path forming the heat exchange chamber 831, an opening 825b is provided which is arranged on the downstream side of the opening 825a and communicates with the opening 825a.

The other configurations of the eighth embodiment are the same as those of the first embodiment.

(Effect of 8th Embodiment)
The effect of the eighth embodiment is the same as that of the fourth and seventh embodiments.

[9th Embodiment]
Next, a ninth embodiment will be described with reference to FIGS. 16 to 18. The ninth embodiment is different from the first embodiment in which the heat exchange chamber 31 is arranged between the pump chamber 12 and the oil chamber 15 in the Z direction, and is outside the pump chamber 12 in the radial direction (A1 direction side). An example in which the heat exchange chamber 931 is arranged in the heat exchange chamber 931 will be described. The same configuration as that of the first embodiment is illustrated with the same reference numerals as those of the first embodiment, and the description thereof will be omitted.

As shown in FIG. 16, the submersible pump 900 according to the ninth embodiment includes a cooling casing 925, a heat exchange chamber 931 and a pump casing 913.

The cooling casing 925 includes an upper cooling casing 925a and a lower cooling casing 925b.

The upper cooling casing 925a is arranged on the outer side (A1 direction side) in the radial direction of the pump casing 913 and surrounds the upper portion of the pump casing 913. The lower cooling casing 925b is arranged on the outer side (A1 direction side) in the radial direction of the pump casing 913 and surrounds the lower portion of the pump casing 913. The pump casing 913 is composed of two members, a main body member 913a surrounding the impeller 14 and a pipe member 913b forming a liquid discharge flow path.

The heat exchange chamber 931 is provided on the outer side (A1 direction side) of the pump chamber 12 in the radial direction so as to surround substantially the entire circumference of the pump chamber 12. Specifically, the heat exchange chamber 931 is provided between the pump casing 913 and the cooling casing 925. In FIG. 17, the impeller 14 is not shown.

As shown in FIG. 18, the heat exchange chamber 931 has a plurality of rib portions 931a extending radially in a plan view and a plurality (six) regions arranged in the circumferential direction. Specifically, the heat exchange chamber 931 includes a plurality (three) regions 931b and a plurality (three) regions 931c. The rib portion 931a is an example of a "guide member" within the scope of the claims.

The region 931b is configured so that the cooling liquid flows in from the first flow path 32 and flows downward (Z2 direction). The region 931c is configured such that the cooling liquid flows in from the region 931b at the end in the Z2 direction, flows upward (in the Z1 direction), and flows out to the second flow path 33. The region 931b and the region 931c are partitioned by the rib portion 931a, and are arranged alternately in the circumferential direction. The rib portion 931a is provided on the outer periphery of each of the pump casing 913 and the oil casing 24.

As shown in FIG. 16, a plurality of (two) sealing members 4c are provided between the pump casing 913 and the cooling casing 925. The sealing member 4c is watertightly sealed between the atmosphere and the heat exchange chamber 931. The seal member 4c is composed of, for example, an O-ring. The seal member 4c is an example of the "seal structure" in the claims.

A sealing member 4d is provided between the pump casing 913 and the oil casing 24. The seal member 4d is watertightly sealed between the pump chamber 12 and the heat exchange chamber 931. The seal member 4d is composed of, for example, an O-ring. The seal member 4d is an example of the "seal structure" in the claims.

A seal member 4e is provided between the main body member 913a and the pipe member 913b. The seal member 4e is watertightly sealed between the pump chamber 12 and the heat exchange chamber 931. The seal member 4e is composed of, for example, an O-ring. The seal member 4e is an example of a "seal structure" within the scope of the claims.

A seal member 4f is provided between the upper cooling casing 925a and the lower cooling casing 925b. The seal member 4f is watertightly sealed between the atmosphere and the heat exchange chamber 931. The seal member 4f is made of, for example, a packing. The seal member 4f is an example of the "seal structure" in the claims.

The other configurations of the eighth embodiment are the same as those of the first embodiment.

(Effect of 9th Embodiment)
The effect of the ninth embodiment will be described.

In the ninth embodiment, as described above, the heat exchange chamber 931 is provided on the outer side (A1 direction side) of the pump chamber 12 in the radial direction so as to surround the pump chamber 12. As a result, it is possible to secure a large heat transfer area between the heat exchange chamber 931 and the pump chamber 12 by using substantially the entire circumference of the outer circumference of the pump casing 913, so that heat exchange can be effectively performed. Further, heat can be effectively exchanged between the coolant in the heat exchange chamber 931 and the fluid outside the submersible pump 900. Further, since the heat exchange chamber 931 can be arranged at a relatively low position, even when the water level outside the submersible pump 900 is lower, between the coolant of the heat exchange chamber 931 and the fluid outside the submersible pump 900. The heat exchange can be performed more effectively. Further, the length of the drive shaft 10a is longer than that in the case where the heat exchange chamber and the pump chamber are arranged along the drive shaft without the heat exchange chamber 931 and the pump chamber 12 overlapping in the axial direction of the drive shaft 10a. Can be shortened. That is, the device can be miniaturized in the axial direction.

The other effects of the ninth embodiment are the same as those of the first embodiment.

[Modification example]
It should be noted that the embodiments disclosed this time are exemplary in all respects and are not considered to be restrictive. The scope of the present invention is shown by the scope of claims rather than the description of the above-described embodiment, and further includes all modifications (modifications) within the meaning and scope equivalent to the scope of claims.

For example, in the above 1st to 9th embodiments, an example in which the submersible pump is a vertical pump is shown, but the present invention is not limited to this. In the present invention, the submersible pump may be a horizontal pump.

Further, in the above 1st to 9th embodiments, an example in which the number of the first flow paths (second flow paths) is one or three is shown, but the present invention is not limited to this. In the present invention, the number of the first flow path (second flow path) may be two or four or more.

Further, in the first to ninth embodiments, an example in which the cooling liquid circulation pump chamber (cooling liquid circulation impeller) is provided between the motor (excluding the drive shaft) and the oil chamber is shown. The present invention is not limited to this. In the present invention, the cooling liquid circulation pump chamber (cooling liquid circulation impeller) may be provided, for example, between the oil chamber and the pump chamber.

Further, in the first to ninth embodiments, an example in which the first flow path is formed so as to extend linearly in the axial direction of the drive shaft is shown, but the present invention is not limited to this. In the present invention, the first flow path may be bent between the heat exchange chamber and the motor cooling chamber instead of extending linearly in the axial direction of the drive shaft.

Further, in the first to fifth embodiments and the seventh to ninth embodiments, examples of flowing the cooling liquid from the inside of the motor cooling chamber are shown, but the present invention is not limited to this. In the present invention, the coolant may flow in from the outside of the motor cooling chamber.

Further, in the first to eighth embodiments, an example is shown in which all of the configurations corresponding to the first housing portion, the second housing portion, the third housing portion, and the fourth housing portion of the present invention are provided. However, the present invention is not limited to this. In the present invention, only a part of the first housing portion, the second housing portion, the third housing portion, and the fourth housing portion of the present invention may be provided.

Further, in the first to ninth embodiments, an example in which an electrode type sensor is provided in the oil chamber is shown, but the present invention is not limited to this. In the present invention, the electrode type sensor may not be provided in the oil chamber. Further, in the present invention, the motor may be configured to include an electrode type sensor or a float type liquid level sensor to detect water intrusion into the motor.

Further, in the first to ninth embodiments, an example in which an axial flow type impeller is provided as an impeller for cooling liquid circulation is shown, but the present invention is not limited to this. In the present invention, the impeller for circulating coolant may be provided with an impeller of a type different from the axial flow type, such as a centrifugal impeller.

Further, in the above 1st to 3rd and 5th to 7th embodiments, examples in which the rib portions are formed radially in a plan view are shown, but the present invention is not limited to this. In the present invention, for example, the rib portion may be formed into a meandering shape, an arc shape, or the like in a plan view.

Further, in the first to ninth embodiments, an example in which an O-ring is used as a sealing member is shown, but the present invention is not limited to this. In the present invention, an elastic member other than the O-ring may be used as the sealing member.

Further, in the first to eighth embodiments, the heat exchange chamber is arranged on the upper side of the pump chamber, and in the ninth embodiment, the heat exchange chamber is arranged on the outer side in the radial direction of the pump chamber. Although an example is shown, the present invention is not limited to this. In the present invention, the heat exchange chambers may be arranged both on the upper side of the pump chamber and on the radial outside of the pump chamber.

Further, in the ninth embodiment, an example in which a heat exchange chamber is provided on substantially the entire circumference of the outer periphery of the pump casing is shown, but the present invention is not limited to this. In the present invention, a heat exchange chamber may be provided so as to partially overlap the outer periphery of the pump casing.

Further, in the ninth embodiment, the present invention shows an example in which the pump casing is composed of two members, a main body member surrounding the impeller and a pipe member forming a liquid discharge flow path. Not limited to this. In the present invention, the main body member surrounding the impeller and the pipe member forming the liquid discharge flow path may be integrally configured.

4, 4a, 4b, 4c, 4d, 4e, 4f Seal member (seal structure)
10 Motor 10a Drive shaft 12 Pump chamber 13a Suction port 13b Discharge port 14 Impeller 15 Oil chamber 15a Mechanical seal 21 Bearing cover (4th housing)
21a Inflow port (first opening on the motor side)
21b Outlet (second opening on the motor side)
22 Cooling housing (3rd housing)
23, 423 Oil housing (first housing)
24 Oil casing (partition member)
25, 725, 825, 925 Cooling casing (second housing)
30 Motor cooling chamber 31,433,731,831,931 Heat exchange chamber 31a Rib (guide member)
32, 432, 832 1st flow path 33, 433, 833 2nd flow path 33b Motor lower flow path 34 Coolant circulation pump chamber 34a, 634a Coolant circulation impeller 51, 351 Storage chamber 52, 352 Liquid level Sensor 100, 200, 300, 400, 500, 600, 700, 800, 900 Submersible pump 431a, 831a Horizontal rib part (guide member)
525 Casing (seal structure, integrated structure)
931a Rib part (guide member)

Claims (19)

With the motor including the drive shaft,
A pump chamber in which an impeller driven by the motor is arranged and provided with a suction port and a discharge port, and a pump chamber.
An oil chamber provided with a mechanical seal having a sliding portion and arranged between the motor and the pump chamber, and an oil chamber.
A motor cooling chamber, which is arranged adjacent to the motor and cools the motor with a coolant,
A heat exchange chamber that is arranged adjacent to the pump chamber and exchanges heat between the coolant and the liquid in the pump chamber by flowing the coolant.
Provided on the outer side in the radial direction of the drive shaft with respect to the oil chamber, the heat exchange chamber and the motor cooling chamber are communicated with each other, and the coolant is supplied from one of the heat exchange chamber and the motor cooling chamber to the other. The first flow path to flow and
A second flow path provided on the outer side in the radial direction with respect to the oil chamber, communicating the heat exchange chamber and the motor cooling chamber, and flowing the cooling liquid in the direction opposite to the first flow path .
A submersible pump chamber provided with a coolant circulation impeller for the coolant driven by the motor and provided in the second flow path between the motor and the oil chamber. pump. The submersible pump according to claim 1, wherein the heat exchange chamber is provided with a watertight seal structure to the outside. According to claim 1 or 2 , the first flow path and the second flow path extend in the axial direction of the drive shaft along the outer periphery of the oil chamber on the outer side of the oil chamber in the radial direction. The described submersible pump. The submersible pump according to any one of claims 1 to 3 , wherein at least one of the first flow path and the second flow path is formed so as to surround substantially the entire circumference of the oil chamber. The second flow path is arranged inside the first flow path in the radial direction, and the coolant circulation impeller transfers the coolant from the heat exchange chamber to the coolant circulation pump chamber. The submersible pump according to any one of claims 1 to 4 , wherein the cooling liquid that has flowed in and has flowed out from the cooling liquid circulation pump chamber is configured to flow into the motor cooling chamber. The second flow path is arranged inside the first flow path in the radial direction, and the coolant circulation impeller transfers the coolant from the motor cooling chamber to the coolant circulation pump chamber. The submersible pump according to any one of claims 1 to 4 , wherein the cooling liquid that has flowed in and has flowed out from the cooling liquid circulation pump chamber is configured to flow into the heat exchange chamber. The submersible pump according to any one of claims 1 to 6 , further comprising one first housing portion provided with the oil chamber, including an oil exchange hole communicating the air with the oil chamber. The first housing portion is configured such that the oil exchange hole and the first flow path and the second flow path provided in the first housing portion do not overlap each other in a plan view. The submersible pump according to claim 7 . Claims 1 to 1, wherein the first flow path is provided at least one, is arranged outside the second flow path in the radial direction, and is formed in an arc shape surrounding the drive shaft in a plan view. 8. The submersible pump according to any one of 8. The first housing portion in which the heat exchange chamber side is opened and the oil chamber is provided, and
The second housing portion in which the first housing portion side is opened and the heat exchange chamber is provided, and the second housing portion.
Further, a partition member arranged between the first housing portion and the second housing portion and partitioning the oil chamber and the heat exchange chamber is provided.
The underwater according to claim 2, wherein the seal structure includes a seal member provided between the first housing portion and the partition member and watertightly seals between the oil chamber and the heat exchange chamber. pump. The first housing portion in which the heat exchange chamber side is opened and the oil chamber is provided, and
The second housing portion in which the first housing portion side is opened and the heat exchange chamber is provided, and the second housing portion.
Further, a partition member arranged between the first housing portion and the second housing portion and partitioning the oil chamber and the heat exchange chamber is provided.
The submersible pump according to claim 2, wherein the seal structure includes an integral structure in which the second housing portion and the partition member are integrally formed. The first housing portion provided with the oil chamber and
The second housing portion provided with the heat exchange chamber and
The third housing portion provided with the coolant circulation pump chamber and the third housing portion.
Further, a fourth housing portion provided between the third housing portion and the motor is provided.
The first flow path and the second flow path have the first housing portion, the second housing portion, the third housing portion, and the fourth housing portion with respect to the pump chamber. The underwater according to any one of claims 1 to 11 , which is formed by stacking the second housing portion, the first housing portion, the third housing portion, and the fourth housing portion in this order. pump. The fourth housing portion includes a motor-side first opening that allows the first flow path to communicate with the motor cooling chamber, and a motor-side second opening that allows the second flow path to communicate with the motor cooling chamber.
The submersible pump according to claim 12 , wherein the first opening on the motor side and the second opening on the motor side are provided at positions deviated from each other in the circumferential direction of the drive shaft, respectively. The fourth housing portion extends along the lower surface of the motor, and the fourth housing portion extends along the lower surface of the motor.
The second flow path extends in the radial direction along the lower surface of the motor between the third housing portion and the fourth housing portion, and one end and the other end are respectively for cooling liquid circulation. The submersible pump according to claim 12 or 13 , comprising a pump chamber and a motor lower flow path connected to the motor cooling chamber. One of claims 12 to 14 , wherein the second housing portion is formed so that the position of the heat exchange chamber in the axial direction of the drive shaft overlaps with the position of the oil chamber in the axial direction. The submersible pump according to item 1. Claims 1 to 15 include a guide member in which the heat exchange chamber regulates the flow of the coolant flowing from the outside in the radial direction and flows along the drive shaft, and also flows out from the outside in the radial direction. The submersible pump according to any one of the above items. The underwater according to claim 16 , wherein the guide member has a gap that becomes a part of the flow path of the cooling liquid at the inner end portion in the radial direction, and includes a plurality of rib portions extending radially in the radial direction. pump. A storage chamber arranged between the motor and the oil chamber,
The submersible pump according to any one of claims 1 to 17 , further comprising a liquid level sensor for detecting a predetermined liquid level of the liquid flowing into and stored in the storage chamber. The submersible pump according to any one of claims 1 to 18 , wherein the heat exchange chamber is provided outside the pump chamber in the radial direction.

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