JP7187374B2 - motor pump - Google Patents

Description

The technology disclosed herein relates to motor pumps.

Patent Literature 1 discloses a submersible motor pump that is composed of a motor section and a pump section and that is immersed in pumped liquid. A motor portion of the submersible motor pump is formed with a circulation flow path for cooling water for cooling the motor. A lid casing is attached to the upper end of the pump casing which houses the impeller of the pump. The lid casing is a plate-like member that separates the motor section and the pump section. The lid casing also defines part of the circulation flow path.

JP 2012-57551 A

The submersible motor pump described in Patent Literature 1 may be immersed in pumped liquid containing earth and sand, for example. Due to durability and wear resistance issues, the lid casing separating the motor section and the pump section is made of cast iron.

Due to the structure of the submersible motor pump, the plate-shaped lid casing also functions as a heat exchange section that exchanges heat between the cooling water and the pumped liquid. However, the cast-iron lid casing described in Patent Document 1 has low thermal conductivity, so the heat exchange efficiency is not very high.

Further, in the lid casing described in Patent Document 1, fins are erected on the surface facing the pump section side. Providing fins increases the heat transfer area, which is advantageous for improving the heat exchange efficiency. Therefore, even if the height of the fins is increased in order to further expand the heat transfer area, the heat is not easily transmitted to the tips of the fins because cast iron fins have a low thermal conductivity. Therefore, the heat exchange efficiency of the lid casing is not significantly improved.

On the other hand, there is a demand for more efficient cooling of the motor.

The technology disclosed herein efficiently cools the motor in the motor pump.

The technology disclosed herein relates to motor pumps. motor pump
a motor unit including a motor and a circulation passage through which a coolant for cooling the motor circulates;
a pump section including an impeller fixed to the shaft of the motor and immersed in pumped liquid;
a partition separating the cooling liquid of the motor section and the pumping liquid of the pump section and conducting heat from the cooling liquid to the pumping liquid;
In the partition wall, a plurality of ridges and grooves extending radially outward from a central portion are formed at intervals on the motor portion side and the pump portion side at corresponding positions in the circumferential direction. formed ,
The ridges or grooves on the motor section side form a rectifying path for rectifying the cooling liquid, and the grooves or ridges on the pump section side form a flow through which the pumped liquid flows. forming a road.

According to this configuration, the partition separating the cooling liquid and the pumping liquid functions as a heat exchange section that exchanges heat between the cooling liquid and the pumping liquid. Due to the plurality of ridges and grooves formed in the partition, the partition has a wavy cross section along the central axis of the shaft. By corrugating the cross section, the partition wall has an enlarged heat transfer area.

Further , the ridges or grooves form a rectifying path on the motor portion side and a flow path on the pump portion side. The cooling liquid and the pumped liquid flow smoothly on the motor section side and the pump section side, respectively, with the partition wall interposed therebetween.

The expansion of the heat transfer area and the rectification of the cooling liquid and pumping liquid increase the heat exchange efficiency of the partition wall. Since the coolant that has received heat from the motor can efficiently dissipate heat in the partition wall, the motor of the motor pump can be efficiently cooled.

The partition wall may have a constant or substantially constant thickness.

By doing so, the thickness of the wall separating the cooling liquid and the pumping liquid is not increased. The heat exchange efficiency of the partition is further enhanced. From the viewpoint of durability and wear resistance, even if the partition wall is made of cast iron, which has a relatively low thermal conductivity, the coolant can be efficiently cooled, and the motor can be efficiently cooled. Further, by forming the partition walls to have a corrugated cross-section, the rigidity of the partition walls can be ensured even if the thickness is reduced. Reducing the thickness of the partition wall is more advantageous for improving the heat exchange efficiency.

The partition extends in a direction perpendicular to the central axis of the shaft, the shaft penetrates the central portion of the partition, and the partition extends radially outward from the central portion. A plurality of rectifying paths may be provided.

Since the partition has a plurality of rectifying paths, the heat transfer area of the partition is further expanded. In addition, the cooling liquid spreads and flows along the plurality of rectifying paths over the entire partition wall. As a result, heat can be efficiently transferred from the cooling liquid to the pumping liquid, and the cooling liquid can be efficiently dissipated.

The rectifying path may be curved in the circumferential direction from the central portion toward the radially outward direction.

By doing so, when the outer diameter of the partition wall is assumed to be constant, when the rectifying paths are curved in the circumferential direction, the rectifying paths extending radially outward from the central portion are more curved than when they are not curved. The channel length can be lengthened. As the length of the flow path increases, the heat transfer area of the partition wall can be increased. The heat exchange efficiency of the partition can be improved without increasing the outer diameter of the partition.

The width of the rectifying path may expand radially outward from the central portion.

By doing so, the kinetic energy can be efficiently converted into pressure energy by the diffuser effect while the cooling liquid is flowing radially outward from the central portion in the rectifying path. The energy loss at the radially outer outlet of the commutation path can be reduced.

A part of the circulation channel may be formed around the shaft, and a circulation vane fixed to the shaft may be arranged in the circulation channel provided around the shaft. .

During operation of the pump, the coolant is forced to flow by rotating the circulation vanes together with the shaft. The cooling liquid circulates between the motor and the partition, and the motor is cooled by the cooling liquid radiated in the partition.

The coolant flowing in the circulation channel formed around the shaft flows along the shaft, and then flows radially outward from the central portion of the partition along a plurality of rectifying paths in the partition. The cooling liquid radially flows along the surfaces of the partition walls, thereby improving the heat exchange efficiency between the cooling liquid and the pumped liquid.

The corrugation of the partition wall is inclined with respect to the central axis of the shaft in a cross section along the central axis of the shaft so that the widths of the concave grooves on the motor section side and the pump section side expand from the bottom toward the opening. You can say that there is.

Depending on the environment in which the motor pump is used, dust or the like contained in the pumped liquid may accumulate in the grooves of the partition wall, reducing the heat exchange efficiency of the partition wall. When the corrugation is inclined with respect to the central axis of the shaft so that the width of the groove increases from the bottom toward the opening as in the above configuration, dirt and the like are collected in the groove by the flow of pumped liquid during operation of the pump. It is easy to scrape out from A high heat exchange efficiency can be maintained by suppressing the accumulation of dust or the like in the concave groove.

As described above, according to the motor pump, the motor can be efficiently cooled.

FIG. 1 is a cross-sectional view illustrating the overall configuration of a submersible motor pump. FIG. 2 is an enlarged cross-sectional view illustrating the configuration of a housing portion between the motor portion and the pump portion. The left figure of FIG. 3 is a plan view of the partition, and the right figure is a bottom view of the partition and the lid. FIG. 4 is a sectional view along IV-IV in FIG. 5 is a plan view of a partition different from that in FIG. 3. FIG. FIG. 6 is a plan view of a partition different from FIGS. 3 and 5. FIG. FIG. 7 is a view corresponding to FIG. 4 showing a modification of the cross section of the partition. FIG. 8 is a view corresponding to FIG. 4 showing a modification of the cross section of the partition.

Embodiments of a submersible motor-pump will be described below with reference to the drawings. The submersible motor-pump described here is exemplary.

(Overall configuration of submersible motor pump)
FIG. 1 illustrates a submersible motor-pump 1 . The submersible motor pump 1 is, for example, a pump installed in a pump tank in a sewage system. The submersible motor pump 1 is immersed in the pumped liquid. The submersible motor-pump 1 includes a motor section 11 having a motor 31 for driving an impeller 21 and a pump section 12 having the impeller 21 . The submersible motor-pump 1 is arranged vertically so that the motor section 11 is on the upper side and the pump section 12 is on the lower side. The submersible motor pump 1 also has a forced cooling specification in which the motor portion 11 is provided with a circulation passage through which the circulating cooling liquid cools the motor 31, the details of which will be described later. Here, the cooling liquid is cooling water in which water is the main component in this configuration example, and an additive for corrosion prevention is added thereto. However, the coolant may be composed of cooling oil.

The motor section 11 includes a motor 31 and a motor casing 32 that houses the motor 31 . A shaft 33 of the motor 31 is arranged to extend in the vertical direction. The shaft 33 protrudes downward from the lower end of the motor casing 32 .

The motor casing 32 has a substantially cylindrical shape with its upper and lower ends opened. A top opening of the motor casing 32 is closed by a lid portion 34 . A bearing 351 is attached to the lower surface of the lid portion 34 , and this bearing 351 supports the upper end portion of the shaft 33 . A motor cover 39 is attached to the lid portion 34 , and a head cover 36 is attached to the motor cover 39 .

The motor section 11 also has an outer casing 37 . The outer casing 37 is arranged to surround the outer circumference of the motor casing 32 . The outer casing 37 has a substantially cylindrical shape with both ends opened, and its upper end is fixed to the motor cover 39 . The outer peripheral surface of the motor casing 32 and the inner peripheral surface of the outer casing 37 form a circular first flow path 38 through which the coolant flows. The first flow path 38 surrounds the motor 31 . The coolant flowing through the first flow path 38 receives heat from the motor 31 .

Lower ends of the motor casing 32 and the outer casing 37 are closed by the housing 4 . Details of the configuration of the housing 4 will be described later. The housing 4 forms part of the motor section 11 .

The pump section 12 includes an impeller 21 attached to the lower end of the shaft 33 and a pump casing 22 that houses the impeller 21 . This submersible motor pump 1 is a centrifugal pump provided with a centrifugal impeller 21 .

The pump casing 22 has a volute 23 in which the impeller 21 is housed. The volute 23 communicates with a suction port 24 opening at the bottom of the pump casing 22 . The volute 23 also communicates with a laterally projecting outlet 25 in the pump casing 22 . The discharge port 25 is connected to a discharge pipe (not shown).

The upper end of the pump casing 22 is open. A peripheral edge portion of the upper end opening of the pump casing 22 is fixed to the housing 4 .

The impeller 21 is not limited to the illustrated example, and various types of impellers can be adopted. A main plate 211 of the impeller 21 is provided with a rear blade 212 that reduces the axial load.

The housing 4 is arranged between the lower ends of the motor casing 32 and the outer casing 37 and the upper end of the pump casing 22 . The housing 4 includes a first member 41 and a second member 42, as also shown in FIG.

The first member 41 is fixed to the lower end of the motor casing 32 and the lower end of the outer casing 37 . The first member 41 has a substantially flat plate shape. The first member 41 closes the lower end opening of the motor casing 32 and the lower end opening of the outer casing 37 . A through hole through which the shaft 33 of the motor 31 passes is formed in the central portion of the first member 41 . A bearing 412 that supports the shaft 33 is held by the first member 41 . A plurality of communication holes 411 communicating with the first flow path 38 are formed in the outer peripheral portion of the first member 41 . 1 and 2, only one communication hole 411 is shown.

The second member 42 is arranged below the first member 41 . The second member 42 has a substantially cylindrical shape. The upper end of the second member 42 is fixed to the lower surface of the first member 41 . The lower end of the second member 42 is fixed to the upper end of the pump casing 22 .

The lower end of the second member 42 is open. A partition wall 6 is attached to the lower end of the second member 42 . The lower end of the second member 42 is closed by the partition wall 6 . The partition 6 also closes the top opening of the pump casing 22 . As will be described later, a lid 7 is interposed between the partition wall 6 and the main plate 211 of the impeller 21 .

A second flow path 421 and a third flow path 422 are formed inside the second member 42 . The second flow path 421 and the third flow path 422 are connected to the first flow path 38 through the communication holes 411 respectively. 1 and 2, the communication hole 411 that connects the second channel 421 and the first channel 38 is not shown. The first flow path 38, the second flow path 421, and the third flow path 422 constitute a circulation flow path through which the coolant circulates.

The partition wall 6 forms part of the third flow path 422 . The partition wall 6 separates the cooling liquid of the motor section 11 and the pumping liquid of the pump section 12 . The partition wall 6 also functions as a heat exchange section that exchanges heat between the cooling liquid and the pumped liquid.

The second flow path 421 and the third flow path 422 communicate with each other around the shaft 33 . That is, part of the circulation flow path is provided around the shaft 33 inside the housing 4 .

The housing 4 accommodates a mechanical seal 5 therein. The mechanical seal 5 seals the shaft 33 by being attached to the shaft 33 . The mechanical seal 5 is arranged at a communicating portion between the second flow path 421 and the third flow path 422 .

A circulation vane 51 is attached to the shaft 33 . The circulation vane 51 is arranged at a communicating portion between the second flow path 421 and the third flow path 422 . When the shaft 33 rotates, the circulation vanes 51 rotate together with the shaft 33 . When the circulation blades 51 rotate, the coolant is forced to flow from the second flow path 421 to the third flow path 422 along the shaft 33 . As a result, as indicated by thick black arrows in FIGS. and partition wall 6. The cooling liquid receives heat from the motor 31 around the motor 31 and radiates heat to the pumped liquid near the partition wall 6 .

(Structure of partition wall)
FIG. 3 shows partition 6 and lid 7 . The left figure of FIG. 3 is a plan view of the partition 6, and the right figure is a bottom view of the partition 6 and the lid 7. As shown in FIG. In other words, the left figure shows the surface of the partition wall 6 on the cooling liquid side, and the right figure shows the surfaces of the partition wall 6 and the lid 7 on the liquid side.

The partition wall 6 is disk-shaped and widens in a direction orthogonal to the shaft 33 . A through hole 61 through which the shaft 33 passes is formed in the central portion of the partition wall 6 . The partition 6 also has a corrugated cross section along the central axis of the shaft 33 in the circumferential direction of the partition 6, as shown in the cross-sectional view of FIG. A ridge 62 projecting from the pump section side to the motor section side is formed on the surface of the partition wall 6 facing the motor section, and the partition wall 6 has a protrusion 62 that protrudes from the pump section side toward the motor section side. A concave groove 63 is formed.

As described above, the partition wall 6 functions as a heat exchange section that exchanges heat between the cooling liquid and the pumped liquid. The heat transfer area of the partition wall 6 can be increased by making the cross section of the partition wall 6 wavy, thereby providing the partition wall 6 with the projection 62 on the motor side and the groove 63 on the pump side.

A plurality of ridges 62 are formed at intervals in the circumferential direction. Each of the plurality of ridges 62 extends radially outward from the edge of the through hole 61 in the partition wall 6 .

A rectifying path 64 for rectifying the cooling liquid is formed between adjacent ridges 62 . Here, as shown in FIG. 2, the projection 62 has a protruding end (that is, upper end) spaced from the wall of the housing 4 at a distance H. As shown in FIG. Since the gap H is relatively narrow, the flow of the coolant flows between the ridges 62 rather than the flow passing between the projecting ends of the ridges 62 and the wall of the housing 4 . Flow through rectifier path 64 becomes dominant. The projecting end of the ridge 62 may be brought into contact with the wall of the housing 4 so that the gap H is eliminated.

Each ridge 62 is curved in the circumferential direction from radially inward to outward. The curved direction of the ridges 62 coincides with the rotational direction of the shaft 33 indicated by the dashed line in FIG. As a result, the plurality of straightening paths 64 extend radially outward from the radially inner side, and each straightening path 64 is curved in the circumferential direction from the radially inner side to the outer side. there is The curving direction of the rectifying path 64 is the direction along the rotation direction of the shaft 33 . As shown in the left diagram of FIG. 3, each rectifying path 64 has a narrow radial inner width W1 and a wide radial outer width W2. The width of each rectifying path 64 gradually increases from the radially inner side toward the outer side.

As described above, the coolant flows along the shaft 33 near the shaft 33 at the mounting position of the mechanical seal 5 from the motor section side to the pump section side. Thereafter, the coolant flows radially inwardly outward along the surface of the partition wall 6 (see black arrows in FIG. 3). Since the cooling liquid flows radially along the surfaces of the partition walls 6 over the entire partition walls 6, the efficiency of heat exchange between the cooling liquid and the pumped liquid through the partition walls 6 is improved.

In addition, since the rectification path 64 is curved in the circumferential direction, the flow path length of the rectification path 64 can be made longer than in the case where the rectification path 64 is not curved. The heat transfer area of the partition wall 6 can be increased by increasing the length of the flow path. This configuration can increase the heat exchange efficiency of the partition wall 6 without increasing the outer diameter of the partition wall 6 .

Furthermore, as the width of the rectifying passage 64 gradually widens, the kinetic energy is converted into pressure energy by the diffuser effect while the coolant flows in the rectifying passage 64 radially outward from the central portion of the partition wall 6 . can be converted efficiently. With this configuration, the energy loss at the radially outward outlet of each rectifying path 64 can be reduced.

A concave groove 63 on the pump portion side of the partition wall 6 corresponds to the ridge 62 . Therefore, a plurality of grooves 63 are formed at intervals in the circumferential direction. Each of the plurality of grooves 63 extends radially outward from the edge of the through hole 61 in the partition wall 6 . Each groove 63 is curved in the circumferential direction from radially inward to outward. The pumped liquid flows radially along the concave grooves 63 .

The thickness of the partition wall 6 is constant or substantially constant as shown in FIG. Since the thickness of the wall separating the cooling liquid flowing along the straightening path 64 formed between the ridges 62 and the pumping liquid flowing inside the concave groove 63 is relatively thin, the cooling liquid and the pumping liquid are separated from each other. promotes heat exchange between The constant or substantially constant thickness of the partition walls 6 and the expansion of the heat transfer area combine to increase the heat exchange efficiency of the partition walls 6 . The partition wall 6 is made of cast iron, which has a relatively low thermal conductivity, from the viewpoint of durability and wear resistance. Even if the partition wall 6 is made of cast iron with low thermal conductivity, the partition wall 6 can efficiently cool the coolant. Moreover, since the cross section of the partition wall 6 is corrugated, the rigidity of the partition wall 6 can be ensured even if the thickness is reduced. If the thickness of the partition wall 6 is made as thin as possible, it is more advantageous for improving the heat exchange efficiency.

Here, as shown in FIG. 4, the corrugation of the partition wall 6 is inclined with respect to the central axis of the shaft 33 in a cross section along the central axis of the shaft 33 (see angle θ). As a result, the width of the groove 63 in the circumferential direction increases from the bottom toward the opening. That is, the width of the groove 63 in the circumferential direction increases from the upper end portion toward the lower end opening in FIG. Although not shown, the radial width of the groove 63 also increases from the bottom toward the opening. In the pump tank in which the submersible motor pump 1 is installed, the pumped liquid contains dust and the like, and the dust and the like may accumulate in the grooves 63 of the partition wall 6 having a corrugated cross section. If the partition wall 6 is formed so that the width of the groove 63 expands toward the opening, dirt and the like are easily scraped out of the groove 63 by the flow of pumped liquid during operation of the submersible motor pump 1 . It is possible to prevent dust and the like from accumulating in the concave groove 63 . It is possible to prevent the heat exchange efficiency of the partition wall 6 from deteriorating due to accumulation of dust and the like in the recessed groove 63 of the partition wall 6 . Here, the inclination angle θ of the waveform can be set to an appropriate angle. The tilt angle θ may be set within a range of 3 to 15°, for example.

Further, forming the corrugations so that the width of the grooves 63 of the partition walls 6 is widened can serve as a draft angle when the partition walls 6 are produced using a mold, which is advantageous from the standpoint of manufacturing the partition walls 6 as well. .

On the motor portion side of the partition wall 6, adjacent ridges 62 form a rectifying passage 64 for the cooling liquid, and on the pump portion side, a groove 63 forms a flow path for pumped liquid. be. These flow paths allow the cooling liquid to flow smoothly on both the motor section side and the pump section side with the partition wall interposed therebetween, thereby increasing the heat exchange efficiency of the partition wall 6 . The coolant can be efficiently cooled, and the motor 31 of the submersible motor pump 1 can be efficiently cooled.

Here, the surface of the partition wall 6 on the side of the pump section is the surface facing the main plate 211 of the impeller 21 . The concave grooves 63 formed on this surface form irregularities on the surface of the partition wall 6 on the side of the pump section. This unevenness increases the power for rotating the impeller 21 . In particular, since the main plate 211 of the impeller 21 is formed with the rear blades 212, the combination of the rear blades 212 and the grooves 63 may significantly increase the power loss of the submersible motor-pump 1. .

Therefore, the submersible motor pump 1 has the lid 7 interposed between the partition wall 6 and the main plate 211 of the impeller 21 . The lid 7 is an annular member that is thinner than the partition wall 6 . At least the surface of the lid 7 facing the main plate 211 of the impeller 21 is flat. The surface of the lid 7 is less uneven than the surface of the partition wall 6 on the pump section side. The lid 7 covers the entire surface of the partition wall 6 on the side of the pump section. Note that the illustration on the right side of FIG. 3 omits part of the lid 7 . A lid 7 is attached to the partition wall 6 . As shown in FIG. 4, a predetermined gap is provided between the lid 7 and the surface of the partition wall 6 on the side of the pump section.

Since the surface of the lid 7 facing the main plate 211 of the impeller 21 is flat, power loss during rotation of the impeller 21 is reduced.

Here, the partition wall 6 is a member that exchanges heat between the cooling liquid and the pumped liquid as described above. If the entire surface of the partition wall 6 is covered with the lid 7, the pumped liquid cannot be supplied to the surface of the partition wall 6 on the side of the pump section. Therefore, through holes 71 and 72 are formed in the lid 7 as shown in the right diagram of FIG. The passage holes 71 and 72 respectively penetrate the lid 7 in the thickness direction and connect the partition wall 6 side with the lid 7 therebetween and the main plate 211 side of the impeller 21 . A plurality of passage holes 71 and 72 are provided in the circumferential direction. The through holes 71 and 72 are evenly arranged in the circumferential direction, although only part of them are shown in FIG. The through hole 71 is provided radially inward. The through hole 72 is provided radially outward.

Between the partition wall 6 and the main plate 211 of the impeller 21, the pumped liquid flows in the radial direction while rotating in the circumferential direction. As indicated by solid arrows in FIG. 2, when the impeller 21 rotates, the pumped liquid flows from the pump section side to the partition wall side through the radially outward passage holes 72, It flows from the partition wall side to the pump portion side through the passage hole 71 . Since the pumped liquid can be sequentially supplied to the partition wall 6 by providing the through holes 71 and 72 on the radially inner side and the outer side, respectively, the heat exchange efficiency between the cooling liquid and the pumped liquid via the partition wall 6 is improved. can be improved.

That is, by interposing the lid 7 between the partition wall 6 and the main plate 211 of the impeller 21 and providing passage holes 71 and 72 in the lid 7, the power loss of the submersible motor pump 1 can be reduced and the motor 31 can be It is compatible with efficient cooling.

(Modified example of partition)
FIG. 5 shows a modification of the partition. The rectifying path 66 provided in the partition wall 601 is not curved in the circumferential direction. The rectifying paths 66 are provided between the adjacent ridges 65 , and the plurality of rectifying paths 66 radially extend from the inner side to the outer side in the radial direction. Each straightening path 66 has a narrow radial inner width and a wide radial outer width. The width of each rectifying path 66 gradually increases from the radially inner side toward the outer side.

FIG. 6 shows another modification of the partition. The rectifying path 68 provided in the partition wall 602 has a curved direction opposite to that of the partition wall 6 in FIG. In other words, the rectifying paths 68 are provided between the adjacent ridges 67 , and the plurality of rectifying paths 68 increase in the rotational direction of the shaft 33 (Fig. 6) is curved in the circumferential direction opposite to the direction shown by the dashed-dotted arrow in FIG. In addition, the width of each rectifying path 68 gradually increases from the radially inner side toward the outer side so that the radially inner width is narrower and the radially outer side is wider.

As shown in FIG. 7 , the corrugation of the partition wall 603 may be formed along the central axis of the shaft 33 in a cross section along the central axis of the shaft 33 . In this configuration, the width of groove 69 is constant from the bottom toward the opening.

Further, as shown in FIG. 8, a ridge 610 and grooves 611 are formed on the surface of the partition wall 604 facing the motor section, and grooves 612 and ridges 613 are formed on the surface facing the pump section. As such, the septum 604 may be configured in corrugations. Although not shown, the partition walls may be wavy in such a manner that concave grooves are formed on the surface facing the motor portion and ridges are formed on the surface facing the pump portion, contrary to FIG. good.

In addition, you may combine each structure mentioned above mutually in the possible range.

Also, the motor pump to which the technology disclosed herein can be applied is not limited to the motor pumps illustrated in FIGS. The technology disclosed herein can be applied to motor pumps with various configurations.

1 submersible motor pump 11 motor section 12 pump section 21 impeller 211 main plate 31 motor 33 shaft 38 first flow path (circulation flow path)
421 second channel (circulation channel)
422 third channel (circulation channel)
6 partitions 601, 602, 603, 604 partitions 62, 65, 67, 610, 613 ridges 63, 69, 611, 612 grooves (flow paths)
64, 66, 68 rectification path 7 lids 71, 72 passage hole

Claims (7)

a motor unit including a motor and a circulation passage through which a coolant for cooling the motor circulates;
a pump section including an impeller fixed to the shaft of the motor and immersed in pumped liquid;
a partition separating the cooling liquid of the motor section and the pumping liquid of the pump section and conducting heat from the cooling liquid to the pumping liquid;
In the partition wall, a plurality of ridges and grooves extending radially outward from a central portion are formed at intervals on the motor portion side and the pump portion side at corresponding positions in the circumferential direction. formed ,
The ridges or grooves on the motor section side form a rectifying path for rectifying the cooling liquid, and the grooves or ridges on the pump section side form a flow through which the pumped liquid flows. A motor pump forming a path.
In the motor pump according to claim 1,
The motor pump, wherein the partition wall has a constant or substantially constant thickness. The motor pump according to claim 1 or 2,
The partition extends in a direction perpendicular to the central axis of the shaft,
The shaft passes through the central portion of the partition,
The partition wall has a plurality of rectifying paths extending radially outward from the central portion. In the motor pump according to claim 3,
The motor pump, wherein the rectifying path is curved in the circumferential direction from the central portion toward the radially outward direction. The motor pump according to claim 3 or 4,
The motor pump, wherein the width of the rectifying path increases radially outward from the central portion. In the motor pump according to any one of claims 1 to 5,
A portion of the circulation flow path is provided around the shaft,
A motor pump in which circulation vanes fixed to the shaft are arranged in a circulation flow path provided around the shaft. In the motor pump according to any one of claims 1 to 6,
The corrugation of the partition wall is inclined with respect to the central axis of the shaft in a cross section along the central axis of the shaft so that the widths of the concave grooves on the motor section side and the pump section side expand from the bottom toward the opening. motor pump.

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