KR20240051237A - motor pump - Google Patents

Abstract

The present invention relates to a motor pump. The motor pump MP includes a rotor holder 200 that holds the rotor 2, and an impeller 1 that is a press-molded product to which the rotor holder 200 is fixed.

Description

motor pump

The present invention relates to a motor pump.

Pump devices comprising a motor and a pump connected by a coupling are known. Such a pump device has a structure that transmits the driving force of the motor to the impeller of the pump through a coupling.

Japanese Patent Publication No. 2000-303986

However, in such a pump device, the pump and motor are arranged side by side, so the installation area becomes large. Meanwhile, in recent years, the demand for compactness (and energy saving) has increased, and as a result, the demand for an integrated structure of the pump and motor has also increased.

Therefore, the purpose of the present invention is to provide a motor pump with a compact structure.

In one aspect, a motor comprising a rotor, a stator disposed radially outside the rotor, a rotor holder holding the rotor, and an impeller that is a press-molded product to which the rotor holder is fixed. A pump is provided.

In one aspect, the rotor holder includes a press-formed annular accommodating portion that accommodates the rotor, and an annular closing plate that closes the accommodating portion.

In one aspect, the rotor holder includes a seal member disposed between the accommodating portion and the blocking plate.

In one aspect, the rotor holder has a filler filled in the receiving portion.

In one aspect, the rotor holder includes a spacer disposed between the receiving portion and the rotor.

In one aspect, the accommodating portion includes an outer annular portion and an inner annular portion disposed radially inside the outer annular portion, and the inner annular portion has a plurality of protrusions formed at a contact portion with the rotor. .

In one aspect, the inner surface of the rotor in contact with the inner annular portion has a polygonal shape.

In one aspect, the motor pump supports the impeller and is provided with a bearing disposed outside the flow path of the impeller, and the bearing includes a rotation side bearing body mounted on the rotor holder, and the rotation side bearing body. It is provided with a fixed side bearing body disposed on the suction side of the side bearing body.

In one aspect, the motor pump includes a stator casing that accommodates the stator and is integrally molded with a resin mold.

In one aspect, the motor pump includes a motor frame that covers the outer peripheral surface of the stator casing and is in contact with the stator.

In one aspect, the rotor and the bearing are disposed in a suction side area of the impeller.

In one aspect, a rotor is provided, a stator disposed on a radial outer side of the rotor, a rotor holder holding the rotor, and an impeller that is a resin molded product in which the rotor holder is integrally molded. A motor pump is provided.

In one aspect, the rotor holder includes an annular accommodating portion formed by a resin mold that accommodates the rotor, and a ring holder that closes the accommodating portion.

In one aspect, the ring holder has a rotation prevention structure formed at a connection portion with the receiving portion.

In one aspect, the rotation prevention structure is an embedded hole in which a portion of the receiving portion is embedded.

In one aspect, the rotation prevention structure is a bent portion that is bent in the shape of the Japanese letter コ.

In one aspect, the rotor holder includes a spacer disposed between the ring holder and the rotor.

In one aspect, the ring holder has a plurality of protrusions formed at a contact portion with the rotor.

In one aspect, the inner surface of the rotor in contact with the ring holder has a polygonal shape.

In one aspect, the motor pump supports the impeller and is provided with a bearing disposed outside the flow path of the impeller, and the bearing includes a rotation side bearing body mounted on the rotor holder, and the rotation side bearing body. It is provided with a fixed side bearing body disposed on the suction side of the side bearing body.

In one aspect, the motor pump includes a stator casing that accommodates the stator and is integrally molded with a resin mold.

In one aspect, the motor pump includes a motor frame that covers the outer peripheral surface of the stator casing and is in contact with the stator.

In one aspect, the rotor and the bearing are disposed in a suction side area of the impeller.

The motor pump has an impeller connected to a rotor holder that holds and supports the rotor. Therefore, there is no need to arrange the pump and motor side by side, and as a result, the motor pump can have a compact structure.

1 is a diagram showing one embodiment of a motor pump.
Fig. 2 is a diagram showing the flow of handling fluid passing through a gap between the rotating side bearing body and the stationary side bearing body.
FIG. 3 is a diagram showing one embodiment of a plurality of grooves formed in the flange portion of the fixed side bearing body.
FIG. 4A is a diagram showing one embodiment of a plurality of grooves formed in the cylindrical portion of the fixed-side bearing body.
Fig. 4B is a diagram showing another embodiment of a groove formed in the cylindrical portion of the fixed side bearing body.
Fig. 4C is a diagram showing another embodiment of a groove formed in the cylindrical portion of the fixed side bearing body.
FIG. 5A is a diagram showing one embodiment of a thrust load reduction structure provided on the rear surface of the impeller.
FIG. 5B is a view of FIG. 5A viewed from arrow line A.
6 is a diagram showing another embodiment of a thrust load reduction structure.
FIG. 7A is a diagram showing a rotor disposed offset with respect to a stator.
FIG. 7B is a diagram showing a rotor disposed offset with respect to the stator.
Figure 8 is a diagram showing one embodiment of a bearing with a tapered structure.
9 is a diagram showing another embodiment of a bearing with a tapered structure.
Figure 10 is a diagram showing a pump unit including a plurality of motor pumps.
11 is a diagram showing another embodiment of a pump unit.
12 is a diagram showing another embodiment of a pump unit.
Fig. 13A is a diagram showing a motor pump as a comparative example.
13B is a diagram showing another embodiment of a motor pump.
13C is a diagram showing another embodiment of a motor pump.
Fig. 14 is a diagram showing one embodiment of a balance adjustment method.
Fig. 15 is a diagram showing one embodiment of a balance adjustment method.
Fig. 16 is a diagram showing one embodiment of a balance adjustment method.
Fig. 17 is a diagram showing one embodiment of a balance adjustment method.
Fig. 18 is a diagram showing one embodiment of a balance adjustment method.
Fig. 19 is a diagram showing another embodiment of the balance adjustment jig.
Fig. 20 is a diagram showing another embodiment of a balance adjustment method.
Figure 21A is a perspective view showing another embodiment of a pump unit.
FIG. 21B is a plan view of the pump unit shown in FIG. 21A.
Fig. 22 is a diagram showing the control flow of the motor pump by the control device.
23 is a diagram showing another embodiment of an impeller.
Figure 24 is a diagram showing another embodiment of the impeller.
Fig. 25 is a view showing a seal member disposed between the cover and the side plate.
Figure 26 is a diagram showing another embodiment of the impeller.
Fig. 27 is a diagram showing another embodiment of a motor pump.
Fig. 28 is a diagram showing another embodiment of a motor pump.
Fig. 29 is a diagram showing another embodiment of a motor pump.
Figure 30 is a diagram showing a motor pump in which various components can be selected depending on operating conditions.
31A is a cross-sectional view of a motor pump according to another embodiment.
FIG. 31B is a view of the motor pump shown in FIG. 31A when viewed from the axial direction.
32A is a cross-sectional view of a motor pump according to another embodiment.
Figure 32b is a front view of the suction casing of the motor pump shown in Figure 32a.
Figure 33 is a diagram showing a pump unit including a motor pump connected in series.
34 is a diagram showing another embodiment of an impeller.
Fig. 35 is a diagram showing another embodiment of a motor pump.
Figure 36 is an enlarged view of the rotor holder.
Fig. 37 is a diagram showing another embodiment of a spacer.
Fig. 38 is a diagram showing a rotor inserted into a rotor holder.
Figure 39 is a diagram showing a rotor inserted into a rotor holder.
Figure 40 is a diagram showing another embodiment of an impeller.
Figure 41 is an enlarged view of the rotor holder.
Fig. 42 is a diagram showing another embodiment of the rotation prevention structure.
Figure 43 is a diagram showing another embodiment of a motor pump.
Figure 44 is a diagram showing another embodiment of a motor pump.
Figure 45 is an enlarged view of the first impeller and the second impeller.
Fig. 46 is a diagram showing another embodiment of the connection structure between the first impeller and the second impeller and the communication shaft.
Figure 47 is a diagram showing another embodiment of a fastener.
Figure 48 is a diagram showing another embodiment of the second bearing.
Fig. 49 is a diagram showing another embodiment of the second bearing.
Fig. 50 is a diagram showing a side plate provided in the motor pump according to the above-described embodiment.
Figure 51 shows another embodiment of the side plate.
Figure 52 is a diagram showing another embodiment of a motor pump.

Hereinafter, embodiments of the motor pump will be described with reference to the drawings. In the following embodiments, identical or equivalent components are given the same reference numerals and redundant descriptions are omitted.

1 is a diagram showing one embodiment of a motor pump. As shown in FIG. 1, the motor pump MP includes an impeller 1, an annular rotor 2 fixed to the impeller 1, and a stator 3 disposed radially outside the rotor 2. ) and a bearing (5) that supports the impeller (1). The impeller 1 has a flow path formed therein, and the bearing 5 is disposed outside the flow path (for example, an inlet flow path) of the impeller 1.

In the embodiment shown in FIG. 1, the motor pump MP is a rotating machine equipped with a permanent magnet type motor, but the type of the motor pump MP is not limited to this embodiment. In one embodiment, the motor pump MP may be provided with an induction type motor or a reluctance type motor. If the motor pump MP has a permanent magnet type motor, the rotor 2 is a permanent magnet. When the motor pump MP is equipped with an induction motor, the rotor 2 is a basket-type rotor.

In the embodiment shown in FIG. 1, the impeller 1 is a centrifugal impeller. More specifically, the impeller 1 includes a disk-shaped main plate 10, a side plate 11 disposed opposite to the main plate 10, and a plurality of blades disposed between the main plate 10 and the side plate 11. (12) is provided. The motor pump MP equipped with the impeller 1 as a centrifugal impeller has excellent positive pressure characteristics compared to pumps such as axial flow pumps and diagonal flow pumps, and can generate high pressure. Additionally, the motor pump MP in this embodiment can contribute to the rotational stability of the impeller 1 by utilizing the pressure difference generated within it.

The side plate 11 has a suction portion 15 formed in its central portion and a main body portion 16 connected to the suction portion 15. The suction portion 15 extends in the direction of the center line CL of the motor pump MP, and the main body portion 16 extends in a direction inclined (more specifically, in a vertical direction) with respect to the center line CL. The center line CL is parallel to the flow direction of the liquid (handled liquid) flowing by the operation of the motor pump MP.

As shown in FIG. 1, the side plate 11 is an annular shape extending from the outer edge 11a (more specifically, the end of the main body 16) of the side plate 11 toward the suction portion 15. It is provided with a protrusion 17. In the embodiment shown in FIG. 1, the main body portion 16 and the protruding portion 17 are formed integrally, but the protruding portion 17 may be a separate member from the main body portion 16.

The rotor 2 has an inner diameter larger than the outer diameter of the protrusion 17, and is fixed to the outer peripheral surface 17a of the protrusion 17. The stator 3 is arranged to surround the rotor 2 and is accommodated in the stator casing 20. The stator casing 20 is disposed outside the impeller 1 in the radial direction.

The motor pump MP has a suction casing (21) and a discharge casing (22) disposed on both sides of the stator casing (20). The suction casing 21 is disposed on the suction side of the impeller 1, and the discharge casing 22 is disposed on the discharge side of the impeller 1. The impeller 1, rotor 2, and bearing 5 are arranged radially inside the stator casing 20 and between the suction casing 21 and the discharge casing 22.

The suction casing 21 has an inlet 21a in its central portion. The discharge casing 22 has a discharge port 22a in its central portion. These suction ports 21a and discharge ports 22a are arranged in a straight line along the center line CL. Therefore, the handling liquid sucked in from the suction port 21a and discharged from the discharge port 22a flows in a straight line.

As shown in FIG. 1, the operator places the stator casing 20 between the suction casing 21 and the discharge casing 22, and inserts the through bolt 25 into the suction casing 21 and the discharge casing 22. ) and fasten the through bolt (25). In this way, the motor pump MP is assembled.

When the motor pump MP is operated, the handling liquid is sucked in from the suction port 21a of the suction casing 21 (see black line arrow in FIG. 1). The rotation of the impeller 1 increases the pressure of the handling liquid, and the handling liquid flows in a direction perpendicular to the center line CL (i.e., centrifugal direction) inside the impeller 1. The liquid discharged to the outside of the impeller 1 collides with the inner peripheral surface 20a of the stator casing 20, and the direction of the liquid is changed. After that, the handling liquid is discharged from the discharge port 22a through the gap between the back surface of the impeller 1 (more specifically, the main plate 10) and the discharge casing 22.

As shown in FIG. 1, the motor pump MP is provided with a return blade 30 disposed on the rear side of the impeller 1. In the embodiment shown in FIG. 1, a plurality of helically extending return blades 30 are provided. These plurality of return blades 30 are fixed to the discharge casing 22 and face the main plate 10 of the impeller 1. By providing the return blade 30, the handling liquid discharged from the impeller 1 is smoothly guided to the discharge port 22a. The return blade 30 contributes to the conversion of the handling liquid discharged from the impeller 1 from velocity energy to pressure energy.

In the embodiment shown in FIG. 1, the motor pump MP is divided into a suction side region Ra, a discharge side region Rb, and an intermediate region Rc between the suction side region Ra and the discharge side region Rb. The suction side area Ra is between the suction casing 21 (more specifically, the suction port 21a of the suction casing 21) and the impeller 1 (more specifically, the side plate 11 of the impeller 1). is the area of The discharge side area Rb is between the discharge casing 22 (more specifically, the discharge port 22a of the discharge casing 22) and the impeller 1 (more specifically, the main plate 10 of the impeller 1). It's an area. A plurality of wings 12 are arranged in the middle region Rc.

The rotor 2 and bearing 5 are arranged in the suction side area Ra of the impeller 1. In this embodiment, the impeller 1 is provided with a side plate 11 having a tapered shape extending from the suction side area Ra toward the discharge side area Rb. Accordingly, a space (dead space) is formed in the suction side area Ra of the impeller 1. According to this embodiment, by arranging the rotor 2 and the bearing 5 in the suction side area Ra, the motor pump MP can have a structure that effectively utilizes the dead space, and as a result, can have a compact structure. You can.

The bearing 5 includes a rotating side bearing body 6 mounted on the protrusion 17 of the side plate 11 and a fixed side bearing body 7 mounted on the suction casing 21. The fixed side bearing body (7) is arranged on the suction side of the rotating side bearing body (6). The rotating side bearing body 6 is a rotating member that rotates with the rotation of the impeller 1, and the fixed side bearing body 7 is a stationary member that does not rotate even when the impeller 1 rotates.

The rotation-side bearing body 6 has a cylindrical portion 6a having an outer diameter smaller than the inner diameter of the protruding portion 17, and a flange portion 6b protruding outward from the cylindrical portion 6a. Therefore, the cross section of the rotation side bearing body 6 has an L-shape. A seal member (for example, O-ring) 31 is disposed between the inner peripheral surface 17b of the protruding portion 17 and the cylindrical portion 6a.

The rotation-side bearing body 6 is mounted on the protruding portion 17 of the impeller 1 with the seal member 31 mounted on the cylindrical portion 6a. By mounting the rotation-side bearing body 6, the rotor 2 is disposed adjacent to the flange portion 6b of the rotation-side bearing body 6.

The fixed side bearing body 7 has a cylindrical portion 7a disposed opposite to the cylindrical portion 6a of the rotating side bearing body 6 and a flange portion 6b of the rotating side bearing body 6. It is provided with an arranged flange portion 7b. The cross section of the stationary bearing body 7 has an L-shape, similar to the cross section of the rotating bearing body 6. Seal members 32 and 33 are disposed between the cylindrical portion 7a of the fixed side bearing body 7 and the suction casing 21. In this embodiment, two seal members 32 and 33 are disposed, but the number of seal members is not limited to this embodiment.

Fig. 2 is a diagram showing the flow of handling liquid passing through a gap between the rotating side bearing body and the stationary side bearing body. Since the pressure of the handling liquid is increased by the rotation of the impeller 1, the pressure of the handling liquid in the discharge side area Rb is greater than the pressure of the handling liquid in the suction side area Ra. Accordingly, a part of the handling liquid discharged from the impeller 1 flows back to the suction side area Ra (see black line arrow in FIG. 2).

More specifically, a part of the handling liquid passes through the gap between the stator casing 20 and the rotor 2, and passes between the flange portion 6b of the rotating side bearing body 6 and the stationary side bearing body 7. It flows into the gap between the flange portions 7b.

FIG. 3 is a diagram showing one embodiment of a plurality of grooves formed in the flange portion of the fixed side bearing body. As shown in FIG. 3, the fixed side bearing body 7 has a plurality of grooves 40 formed in the flange portion 7b. These plurality of grooves 40 are formed on the surface of the flange portion 7b opposite to the flange portion 6b of the rotation side bearing body 6. The plurality of grooves 40 are formed to generate dynamic pressure of the handling liquid in the gap between the flange portions 7b and 6b. In this embodiment, the plurality of grooves 40 are spiral grooves extending in a spiral shape. In one embodiment, the plurality of grooves 40 may be radial grooves extending radially. By forming the plurality of grooves 40, the bearing 5 can support the thrust load of the impeller 1 without contact.

In the embodiment shown in FIG. 3, the plurality of grooves 40 are formed in the flange portion 7b. However, in one embodiment, the plurality of grooves 40 are formed in the flange portion of the rotation side bearing body 6. It may be formed in (6b). Even with this formation, the bearing 5 can support the thrust load of the impeller 1 in a non-contact manner.

FIG. 4A is a diagram showing one embodiment of a plurality of grooves formed in the cylindrical portion of the fixed-side bearing body. FIG. 4A shows a plurality of grooves 41 when viewed from the center line CL direction. The fixed side bearing body 7 may have a plurality of grooves 41 formed in the cylindrical portion 7a along the circumferential direction of the cylindrical portion 7a. In the embodiment shown in FIG. 4A, the plurality of grooves 41 are arranged at equal intervals, but may be arranged at unequal intervals.

These plurality of grooves 41 are formed on the surface of the cylindrical portion 7a opposite to the cylindrical portion 6a of the rotation side bearing body 6, and are formed on the cylindrical portion 7a (i.e., in the center line CL direction). It extends parallelly. In the embodiment shown in FIG. 4A, each of the plurality of grooves 41 has an arc-shaped concave shape when viewed from the center line CL direction. The shape of the plurality of grooves 41 is not limited to this embodiment. In one embodiment, each of the plurality of grooves 41 may have a concave shape when viewed from the center line CL direction.

4B and 4C are diagrams showing another embodiment of a groove formed in the cylindrical portion of the fixed side bearing body. As shown in FIGS. 4B and 4C , the fixed-side bearing body 7 has an annular groove 42 formed in the cylindrical portion 7a along the circumferential direction of the cylindrical portion 7a. The groove 42 is formed in a part of the cylindrical portion 7a and has a concave shape when viewed from a direction perpendicular to the center line CL direction (see FIGS. 4B and 4C). Cylindrical portions 7a exist at both ends 42a and 42a of the groove 42 in the center line CL direction. With this structure, even if a radial load acts on the impeller 1, the fixed side bearing body 7 (more specifically, the cylindrical portion 7a) moves through the rotating side bearing body 6 to the impeller ( 1) can be clearly supported. Additionally, the length of the groove 42 in the center line CL direction is not particularly limited. In the embodiment shown in FIGS. 4B and 4C, the fixed side bearing body 7 has a single groove 42. However, in one embodiment, the fixed side bearing body 7 runs along the center line CL direction. You may have a plurality of grooves 42 arranged.

The handling liquid that has passed through the gap between the flange portion 6b and the flange portion 7b flows into the gap between the cylindrical portion 6a and the cylindrical portion 7a. When the rotation side bearing body 6 rotates together with the impeller 1, viscous resistance is generated in the handling liquid flowing through this gap. This viscous resistance may adversely affect the operating efficiency of the motor pump MP.

As shown in the above-described embodiment, by forming a plurality of grooves 41 (or grooves 42), the size of the narrow region formed in the gap between the cylindrical portions 6a and 7a is reduced. Therefore, the viscous resistance occurring in the handling liquid can be reduced. Additionally, by forming a plurality of grooves 41 (or grooves 42), dynamic pressure of the handling liquid is generated, and the bearing 5 can support the radial load of the impeller 1 in a non-contact manner. The effect of reducing viscous resistance by reducing the size of the narrow region formed between the flange portion 6b and the flange portion 7b can also be achieved by providing a plurality of grooves 40 (see FIG. 3).

In the embodiment shown in FIGS. 4A to 4C, the grooves 41 and 42 are formed in the cylindrical portion 7a. However, in one embodiment, the grooves 41 and 42 are formed in the rotation side bearing body 6. It may be formed in the cylindrical portion 6a. Even with this configuration, the bearing 5 can support the radial load of the impeller 1 without contact.

As shown in FIG. 2, the handling fluid that has passed through the gap between the cylindrical portion 6a of the rotating side bearing body 6 and the cylindrical portion 7a of the stationary side bearing body 7 is the side plate of the impeller 1. It passes through the gap between (11) and the suction casing (21) and is returned to the suction side of the motor pump MP. In this embodiment, the bearing 5 is arranged in the path of the leakage flow of the handling liquid. With this configuration, a part of the handling liquid flows into the minute gap between the rotating side bearing body 6 and the stationary side bearing body 7, and as a result, the motor pump MP can suppress leakage of the handling liquid. .

As described above, the pressure of the handling liquid in the discharge side area Rb is greater than the pressure of the handling liquid in the suction side area Ra. Therefore, a thrust load acts on the impeller 1 from the discharge port 22a of the discharge casing 22 toward the suction port 21a of the suction casing 21 (see arrow on white background in FIG. 1). The motor pump MP according to this embodiment has a structure that reduces the thrust load.

FIG. 5A is a diagram showing one embodiment of a thrust load reduction structure provided on the rear surface of the impeller. FIG. 5B is a view of FIG. 5A viewed from arrow line A. As shown in FIGS. 5A and 5B, the motor pump MP is provided with a thrust load reduction structure 45 provided on the back of the impeller 1 (more specifically, the main plate 10). In the embodiment shown in FIGS. 5A and 5B , the thrust load reduction structure 45 is a plurality of back surface blades 46 provided on the main plate 10 and extending helically. These plurality of back blades 46 can generate a load in the opposite direction to the thrust load by rotating the impeller 1. As a result, the thrust load reduction structure 45 can reduce the thrust load generated in the motor pump MP.

6 is a diagram showing another embodiment of a thrust load reduction structure. As shown in FIG. 6, the thrust load reduction structure 45 is formed along the circumferential direction of the impeller 1 (more specifically, the main plate 10) and extends toward the center side of the impeller 1. A plurality of notch structure may be used. In the embodiment shown in FIG. 6, a plurality of notches 47 are formed in the main plate 10 of the impeller 1. By forming the plurality of notches 47, the contact area of the liquid to be handled with the main plate 10 is reduced. As a result, the thrust load reduction structure 45 can reduce the thrust load generated in the motor pump MP. Although not shown, the embodiment shown in FIG. 5 and the embodiment shown in FIG. 6 may be combined.

In this embodiment, the impeller 1 always receives a thrust load from the discharge side toward the suction side. Additionally, the bearing 5 supports the impeller 1 that generates rotational force. Accordingly, the parallelism of the impeller 1 itself is maintained, and rattling of the impeller 1 can be suppressed. As a result, the motor pump MP can stably continue its operation by simply arranging the single bearing 5 in the suction side area Ra (i.e., single bearing structure).

In one embodiment, at least one of the impeller 1 and the bearing 5 may be made of a lightweight material. Lightweight materials include resins or metals with a low specific gravity (eg, aluminum alloy, magnesium alloy, titanium alloy, etc.). With this structure, the weight of the motor pump MP itself can be reduced, and further compaction of the bearing 5 (and the impeller 1) can be realized. In addition, the materials of the members in contact with the liquid (i.e., liquid contact members), such as the impeller 1 and the bearing 5, are not particularly limited and can be changed to any material as appropriate depending on the quality of the liquid.

Additionally, in this embodiment, the plurality of return blades 30 (see FIG. 1) can reduce the radial load generated on the impeller 1. The plurality of return blades 30 are arranged at equal intervals along the circumferential direction of the discharge port 22a. With this arrangement, the radial load is distributed evenly, and as a result, the radial load occurring on the impeller 1 is reduced.

In this embodiment, the motor pump MP is equipped with a permanent magnet type motor. Therefore, when the motor pump MP is started, a certain load is applied to the bearing 5 to convert the repulsive force resulting from magnetic force into rotational force. This load is the force generated in the rotor (2), and the bearing (5) supports this load.

7A and 7B are diagrams showing a rotor disposed offset with respect to a stator. As shown in FIG. 7A, when the rotor 2 is disposed offset to the discharge side with respect to the stator 3, the impeller 1 is affected by the magnetic force generated between the rotor 2 and the stator 3. Due to the influence of , the rotating side bearing body 6 receives a force acting in a direction approaching the stationary side bearing body 7 (see arrow in FIG. 7A). With this arrangement, the thrust load of the rotating bearing body 6 acting on the stationary bearing body 7 can be adjusted (increased).

As shown in FIG. 7B, when the rotor 2 is arranged to be shifted toward the suction side with respect to the stator 3, the impeller 1 is affected by the magnetic force generated between the rotor 2 and the stator 3. Due to the influence of , the rotating side bearing body 6 receives a force acting in a direction away from the stationary side bearing body 7 (see Fig. 7b). With this arrangement, the thrust load of the rotating bearing body 6 acting on the stationary bearing body 7 can be adjusted (reduced).

Figure 8 is a diagram showing one embodiment of a bearing with a tapered structure. In the embodiment shown in FIG. 8, the bearing 5 is such that the gap between the rotating side bearing body 6 and the stationary side bearing body 7 extends from the suction side toward the discharge side along the center line CL (i.e., of the impeller 1). It has a tapered structure extending in a direction approaching the center portion. As shown in FIG. 8, the rotating bearing body 6 and the stationary bearing body 7 each have inclined surfaces 50 and 51 that face each other. With this configuration, the bearing 5 can concentrate the radial load and thrust load acting on the rotating side bearing body 6 and the stationary side bearing body 7 on the inclined surfaces 50 and 51, so that the bearing (5) may have a simple structure.

9 is a diagram showing another embodiment of a bearing with a tapered structure. In the embodiment shown in FIG. 9, the bearing 5 is such that the gap between the rotating side bearing body 6 and the fixed side bearing body 7 extends from the suction side toward the discharge side along the center line CL (i.e., of the impeller 1). It has a tapered structure extending in a direction away from the center portion. As shown in Fig. 9, the rotating bearing body 6 and the stationary bearing body 7 each have inclined surfaces 53 and 54 that face each other.

Figure 10 is a diagram showing a pump unit including a plurality of motor pumps. As shown in FIG. 10, the pump unit PU may be provided with a plurality of motor pumps MP arranged in series and an inverter 60 that controls each operation of the plurality of motor pumps MP. In the embodiment shown in FIG. 10, each of the plurality of motor pumps MP has the same structure as that shown in the above-described embodiment. Therefore, detailed description of the motor pump MP is omitted.

In the embodiment shown in FIG. 10, the pump unit PU is provided with three motor pumps MP, but the number of motor pumps MP is not limited to this embodiment. As described above, the suction port 21a and the discharge port 22a of the pump unit PU are arranged in a straight line along the center line CL. Therefore, a plurality of motor pumps MP can be continuously arranged in a straight line, and the pump unit PU can easily have a multi-stage motor pump structure.

As shown in FIG. 10, between the suction casing 21 disposed adjacent to the first-stage impeller 1A and the discharge casing 22 disposed adjacent to the third-stage impeller 1C, there are two intermediate A casing 61 is disposed. A second-stage impeller 1B is disposed between these intermediate casings 61 and 61. Each of the intermediate casings 61, 61 has a common (i.e. similar) structure to that of the suction casing 21. The operator places the intermediate casings 61, 61 between the suction casing 21 and the discharge casing 22, and inserts the through bolt 25 into these suction casings 21, intermediate casings 61, 61, and The pump unit can be assembled by inserting and fastening it into the discharge casing 22.

As shown in Fig. 10, one inverter 60 is connected to the stator 3 of the plurality of motor pumps MP. The inverter 60 can independently control each of the plurality of motor pumps MP. Accordingly, the operator can operate at least one motor pump MP at any timing according to the operating conditions of the pump unit.

11 and 12 are views showing another embodiment of the pump unit. In the embodiment shown in FIGS. 11 and 12, the pump unit PU is provided with a plurality of motor pumps MP arranged in parallel. Although shown briefly in FIG. 11 , each of these plurality of motor pumps MP is installed inside the pipe 65 . In FIG. 11, four motor pumps MP are provided, but the number of motor pumps MP is not limited to this embodiment. As shown in Fig. 12, three motor pumps MP may be provided.

Fig. 13A is a diagram showing a motor pump as a comparative example. 13B and 13C are diagrams showing another embodiment of a motor pump. As shown in FIG. 13A, the motor pump as a comparative example has a rotating shaft RS, but the motor pump MP according to the present embodiment does not have a rotating shaft RS. Instead, the impeller 1 has a rounded convex portion 70 disposed in its central portion.

In the embodiment shown in FIG. 13B, the impeller 1 has a convex portion 70A having a first radius of curvature, and in the embodiment shown in FIG. 13C, the impeller 1 has a first radius of curvature and has a convex portion 70B having a different second radius of curvature. Hereinafter, the convex portions 70A and 70B may be simply referred to as the convex portion 70 without distinction.

The convex portion 70 is disposed at the center of the main plate 10 and is formed integrally with the main plate 10. In one embodiment, the convex portion 70 may be a member different from the main plate 10. In this case, the convex portions 70 with different radii of curvature may be exchanged depending on the operating conditions of the motor pump.

The tip 71 of the convex part 70 has a smooth convex shape, and the handling liquid flowing into the impeller 1 contacts the tip 71 of the convex part 70. By providing the convex portion 70, the handling liquid is smoothly and efficiently guided to the blade 12 without impeding its flow. On the other hand, in the motor pump as a comparative example, the rotating shaft RS is fixed to the impeller with a nut Nt, so there is a risk that the flow of the handling liquid may be obstructed by the nut Nt (and the rotating shaft RS).

The convex portion 70A shown in FIG. 13B has a larger radius of curvature than the radius of curvature of the convex portion 70B shown in FIG. 13C. By increasing the radius of curvature of the convex portion 70, the distance between the convex portion 70 and the side plate 11 becomes smaller. Conversely, by reducing the radius of curvature of the convex portion 70, the distance between the convex portion 70 and the side plate 11 increases. In this way, by changing the radius of curvature of the convex portion 70, the size of the flow path of the impeller 1 for the liquid to be handled can be adjusted. The flow path of the impeller 1 shown in FIG. 13C is larger than the flow path of the impeller 1 shown in FIG. 13B.

According to this embodiment, since the motor pump MP does not have a rotating shaft, the number of parts can be reduced, and the size of the flow path can also be adjusted. Additionally, since there is no need to provide a rotating shaft, the impeller 1 can have a compact size. As a result, the entire motor pump MP can have a compact size.

The motor pump rotates the impeller 1 at high speed through its operation. If the position of the center of gravity of the impeller 1 is shifted, the impeller 1 rotates at high speed in an eccentric state. As a result, there is a risk that noise will be generated and, in the worst case, the motor pump may break down.

Therefore, the operator performs a balance (dynamic balance) adjustment method to determine the position of the center of gravity of the impeller 1 to a desired position. As shown in FIG. 13A, when the rotation axis RS is installed in the impeller, it is necessary to install the rotation axis RS in the test machine and rotate the impeller together with the rotation axis RS. In this embodiment, since the rotating shaft RS is not installed in the impeller 1, the operator can perform the balance adjustment method described below.

14 to 18 are diagrams showing one embodiment of a balance adjustment method. As shown in FIG. 14, first, the operator performs a process of forming a through hole 10a in the center of the impeller 1 (more specifically, the main plate 10). After that, as shown in FIG. 15, the operator inserts the shaft body 76 of the balance adjustment jig 75 into the through hole 10a. The shaft body 76 of the balance adjustment jig 75 corresponds to a rotation shaft.

Afterwards, as shown in FIG. 16, the operator places the fixture 77 on the rear side of the impeller 1 and fastens the shaft body 76 to the fixture 77. In this state, the operator determines the position of the center of gravity of the impeller 1 while rotating the impeller 1 with the balance adjustment jig 75, and performs a process of adjusting the position of the center of gravity. In this way, the balance adjustment jig 75 has a structure that supports the center of the impeller 1. Therefore, the balance adjustment jig 75 may also be called a center support adjustment jig.

After determining the position of the center of gravity of the impeller 1 to the desired position, the operator pulls out the shaft body 76 of the balance adjustment jig 75, and then inserts the center cap 80 into the through hole 10a, The through hole 10a is closed (see FIGS. 17 and 18). The center cap 80 has a rounded shape, similar to the convex portion 70 according to the embodiment shown in FIGS. 13B and 13C. Accordingly, the handling liquid is smoothly and efficiently guided to the blades 12 without its flow being impeded.

Fig. 19 is a diagram showing another embodiment of the balance adjustment jig. In the embodiment shown in FIG. 18, the balance adjustment jig 75 has a structure that supports the center of the impeller 1. In the embodiment shown in FIG. 19, the balance adjustment jig 85 includes a supporter 86 that supports the rotation side bearing body 6 of the bearing 5, and a shaft portion 87 fixed to the supporter 86. It is available. In this way, the balance adjustment jig 85 has a structure that supports the end of the impeller 1. Therefore, the balance adjustment jig 85 may also be called an edge support adjustment jig.

The supporter 86 has an annular shape with an outer diameter smaller than the inner diameter of the rotation side bearing body 6. By inserting the supporter 86 into the rotation side bearing body 6, the balance adjustment jig 85 is: The impeller (1) is supported via the rotation side bearing body (6). In this state, the operator performs a process of rotating the impeller 1 together with the balance adjustment jig 85. Thereafter, the operator determines the position of the center of gravity of the impeller 1 while rotating the impeller 1, and performs a process of adjusting the position of the center of gravity.

According to the embodiment shown in FIG. 19, there is no need for the operator to form the through hole 10a. Also in the embodiment shown in Fig. 19, the impeller 1 may have a convex portion 70 formed at its center position (see Figs. 13A and 13B).

Fig. 20 is a diagram showing another embodiment of a balance adjustment method. As shown in FIG. 20, the rotor 2 includes an annular iron core 2a and a plurality of magnets 2b embedded in the iron core 2a. The plurality of magnets 2b are arranged at equal intervals along the circumferential direction of the rotor 2 (more specifically, the iron core 2a). The operator performs a process of forming a plurality of weight insertion holes 90 along the circumferential direction of the rotor 2. The process of forming this weight insertion hole 90 is performed when manufacturing the iron core 2a.

The weight insertion hole 90 is formed between adjacent magnets 2b. The operator determines the current center of gravity position of the impeller 1 by executing a process for determining the position of the center of gravity of the impeller 1. When the position of the center of gravity of the impeller 1 is shifted, the operator inserts the weight 91 into at least one of the plurality of weight insertion holes 90 and performs a process of adjusting the position of the center of gravity.

In one embodiment, when the position of the center of gravity of the impeller 1 is shifted, the operator causes the position of the center of gravity of the impeller 1 to shift instead of inserting the weight 91 into the weight insertion hole 90. You can remove the excess weight.

Figure 21A is a perspective view showing another embodiment of a pump unit. FIG. 21B is a plan view of the pump unit shown in FIG. 21A. As shown in FIGS. 21A and 21B, the pump unit PU includes a plurality of motor pumps MP (three in this embodiment), a control device 100 that operates the plurality of motor pumps MP at variable speeds, and a control device It is electrically connected to 100 and is provided with a current sensor 101 that detects the current supplied to the plurality of motor pumps MP.

In this embodiment, two current sensors 101 are disposed, but at least one current sensor 101 may be disposed. Examples of the current sensor 101 include Hall elements and CTs (current transducers).

The pump unit PU is provided with a power line 105 and a signal line 106 extending from a plurality of motor pumps MP, and a protective cover 107 that protects the current sensor 101, the power line 105, and the signal line 106. I'm doing it. The power line 105 and signal line 106 are electrically connected to the inverter 60.

Between the plurality of motor pumps MP, U-phase, V-phase, and W-phase copper bars (in other words, conductive plates, copper plates) 108 are stretched, and the current sensor 101 is one of these copper bars 108. Connected to the dog. Each motor pump MP is provided with a terminal block 102, and a copper bar 108 is connected to the terminal block 102.

The control device 100 is electrically connected to the inverter 60 and is configured to control the operation of the motor pump MP through the inverter 60. The control device 100 may be placed outside the inverter 60 or may be placed inside the inverter 60 .

The control device 100 includes a signal receiving unit 100a that receives a signal from the current sensor 101 through a signal line 106, a storage unit 100b that stores information about the operation of the motor pump MP or an operation program, and , It is provided with a control unit 100c that controls the operation of the motor pump MP based on the data received from the signal receiving unit and the data stored in the storage unit.

In this embodiment, the pump unit PU is provided with one inverter 60 for a plurality of motor pumps MP, but the pump unit PU is provided with a number of inverters 60 corresponding to the number of motor pumps MP. You can do it. When a plurality of motor pumps MP are arranged, each of the plurality of inverters 60 controls each operation of the plurality of motor pumps MP by the control device 100.

As described above, the motor pump MP has a compact structure that effectively utilizes dead space. Therefore, by connecting these plural motor pumps MP in series, the pump unit PU can operate at a high lift without increasing its installation area.

The motor pump MP is a rotating machine with a permanent magnet motor. Such a motor rotates uncontrollably by forcibly applying voltage at startup. Control of the rotational speed of the motor pump MP by the inverter 60 is started immediately, and then normal operation of the motor pump MP is started.

In this embodiment, the pump unit PU is equipped with a plurality of motor pumps MP. Therefore, before starting control of the rotational speed of the motor pump MP, there is no problem if the rotational speed difference between the plurality of motor pumps MP is resolved. However, if the rotational speed difference is not resolved, startup failure of the motor pump MP may occur. There are concerns.

In general, as the number of magnetic poles of the rotor 2 increases, the motor pump MP rotates smoothly, and the rotation speed difference between a plurality of motor pumps MP becomes easier to eliminate. The motor pump MP in this embodiment has a structure that forms a flow path inside the rotor 2, and the outer diameter of the rotor 2 is designed to be large.

When the outer diameter of the rotor 2 is large, the size of the outer circumferential direction of the rotor 2 increases, so a plurality of magnets can be easily arranged and the number of magnetic poles can be increased. With this configuration, the pump unit PU can eliminate the rotational speed difference between the plurality of motor pumps MP. Additionally, in this embodiment, by using an inexpensive flat magnet, the cost of the rotor 2 can be reduced compared to a general motor using a curved magnet.

In addition, in this embodiment, the motor pump MP has a canned motor structure in which the stator 3 is accommodated in the stator casing 20, and the distance between the rotor 2 and the stator 3 is shorter than that of a general motor. , big. Accordingly, the motor pump MP can reduce torque ripple, which means the fluctuation range of torque, and as a result, the pump unit PU can eliminate the rotational speed difference between the plurality of motor pumps MP.

In this way, the pump unit PU can eliminate the rotational speed difference, but it is desirable to operate the motor pump MP more stably during startup and/or normal operation of the motor pump MP.

Therefore, the control method of the motor pump MP will be described below. In this embodiment, a plurality of motor pumps MP are connected in series. In this case, if the handling liquid contains foreign matter, there is a risk that the foreign matter may become entangled in the motor pump MP (in particular, the first motor pump MP), and as a result, the operation of the pump unit PU may be impaired by the foreign matter. Additionally, there is a risk that the rotational speed difference between the plurality of motor pumps MP may not be resolved for some reason.

Fig. 22 is a diagram showing the control flow of the motor pump by the control device. As shown in step S101 of FIG. 22, the control device 100 electrically connected to the inverter 60 controls a plurality of signals during the current operation of the motor pump MP based on the output current of the inverter 60. The current value of the motor pump MP (more specifically, the sum of the current values of each motor pump MP) is measured.

Thereafter, the control device 100 calculates the lower limit current value based on the assumed current value during normal operation of the motor pump MP (more specifically, during startup and normal operation), The sum of the measured current values (measured current value Amax) is compared with the predetermined lower limit current value (see step S102). In one embodiment, the storage unit 100b of the control device 100 stores the assumed current value of each motor pump MP and the assumed current values of a plurality of motor pumps MP. The storage unit 100b may calculate the assumed current values of a plurality of motor pumps MP from the assumed current values of each motor pump MP.

The control device 100 may determine the “assumed current value assumed during normal operation” based on at least one of the rated current value and the allowable current value of each motor pump MP, and may be used for multiple motor pump MPs. Based on the current value during operation, the “assumed current value assumed during normal operation” may be determined.

In one embodiment, the control device 100 determines the lower limit current value based on the number of motor pumps MP. For example, the lower limit current value is obtained by the following calculation formula.

Lower limit current value = assumed current value of multiple motor pumps MP × (1-1/number of motor pumps n)

In this embodiment, since three motor pumps MP are arranged, the lower limit current value is 2/3 of the assumed current value.

After step S102, the control device 100 compares the calculated lower limit current value and the measured current value (see step S103). More specifically, the control device 100 determines whether the measured current value is lower than the lower limit current value (measured current value Amax > lower limit current value).

If the measured current value is lower than the lower limit current value (see "Yes" in step S103), in this embodiment, the measured current value is less than 2/3 of the assumed current value (i.e., lower limit current value). In this case, the control device 100 determines that an abnormality has occurred in at least one of the plurality of motor pumps MP (see step S104). If the measured current value does not fall below the lower limit current value (see "No" in step S103), the control device 100 repeats steps S102 and S103.

When the control device 100 determines that an abnormality has occurred, the control device 100 may issue an alarm while continuing to operate the motor pump MP, or may stop the operation of the motor pump MP and issue an alarm.

Such a control flow may be performed when the motor pump MP is started, or may be performed during normal operation of the motor pump MP. When performing a control flow when the motor pump MP is started, the measured current value corresponds to the starting current value when the plurality of motor pumps MP are started, and the assumed current value is the normal current value of the plurality of motor pump MPs. This is the current value assumed at startup.

When performing a control flow during normal operation of the motor pump MP, the measured current value corresponds to the operating current value during normal operation of the plurality of motor pumps MP, and the assumed current value is the operating current value of the plurality of motor pumps MP. This is the current value assumed during normal normal operation.

The starting current value and the operating current value may be the same or different. Likewise, the assumed current value assumed during normal startup and the assumed current value assumed during normal normal operation may be the same or different.

In one embodiment, the control device 100 may determine the assumed current value based on the flow rates on the discharge side of the plurality of motor pumps MP. In this case, the pump unit PU is equipped with a flow rate sensor (not shown) that detects the flow rate of the handling liquid, and the flow rate sensor is electrically connected to the control device 100.

The storage unit 100b of the control device 100 stores data showing the correlation between the flow rate of the handling liquid during normal operation and the current supplied to the plurality of motor pumps MP during normal operation. . The control device 100 determines an assumed current value based on this data, and calculates a lower limit current value based on the determined assumed current value. An example of a calculation formula for the lower limit current value is the above calculation formula.

The control device 100 compares the measured current value and the lower limit current value during normal operation of the plurality of motor pumps MP, and when the measured current value is lower than the lower limit current value, at least one of the plurality of motor pumps MP It is determined that something is wrong with one device.

In one embodiment, the control device 100 may determine the assumed current value based on the pressure on the discharge side of the plurality of motor pumps MP. In this case, the pump unit PU is equipped with a pressure sensor (not shown) that detects the pressure of the handling liquid, and the pressure sensor is electrically connected to the control device 100.

The storage unit 100b of the control device 100 stores data showing the correlation between the pressure of the handling liquid and the current supplied to the plurality of motor pumps MP during normal operation. The control device 100 determines an assumed current value based on this data, and calculates a lower limit current value based on the determined assumed current value. An example of a calculation formula for the lower limit current value is the above calculation formula.

The control device 100 compares the measured current value and the lower limit current value during normal operation of the plurality of motor pumps MP, and when the measured current value is lower than the lower limit current value, at least one of the plurality of motor pumps MP It is determined that something is wrong with one device.

In the embodiment shown in FIGS. 21A and 21B, the pump unit PU is a current sensor disposed between the first motor pump MP (first motor pump MP) and the second motor pump MP (second motor pump MP). (101) (first current sensor 101), and a current sensor 101 (second current sensor 101) disposed between the second motor pump MP and the third motor pump MP (third motor pump MP) ) is provided.

Therefore, the control device 100 measures the current value (that is, the measured current value Aa1) of the first motor pump MP based on the signal sent from the first current sensor 101 and the second current sensor 101 ), the sum of the measured current value Aa1 of the first motor pump MP and the measured current value Aa2 of the second motor pump MP (i.e., measured current value Ab (=Aa1+Aa2)) can be measured. there is.

The control device 100 compares the measured current value Aa1 with the assumed current value assumed during normal operation (during start-up and normal operation) of each motor pump MP, and the measured current value Aa1 is lower than the assumed current value. In the case (Aa1<assumed current value), it is determined that an abnormality has occurred in the first motor pump MP.

The control device 100 compares the measured current value Aa1 with the assumed current value assumed during normal operation (during start-up and normal operation) of each motor pump MP, and the measured current value Aa1 is greater than the assumed current value. (Aa1>assumed current value), and if the value obtained by subtracting the measured current value Aa1 from the measured current value Ab (i.e., Ab-Aa1) is smaller than the assumed current value ((Ab-Aa1)<assumed current value), 2 It is determined that an error has occurred in the motor pump MP. The value obtained by subtracting the measured current value Aa1 from the measured current value Ab corresponds to the measured current value Aa2.

When the control device 100 determines that the measured current value Amax is lower than the lower limit current value and that no abnormality has occurred in the first motor pump MP and the second motor pump MP, the control device 100 determines that an abnormality has occurred in the third motor pump MP. Decide that this is happening.

When the pump unit PU is equipped with four motor pumps MP connected in series, the pump unit PU has a current sensor disposed between the third motor pump MP and the fourth motor pump MP (fourth motor pump MP). 101) (third current sensor 101).

Based on the signal sent from the third current sensor 101, the control device 100 determines the measured current value Aa1 of the first motor pump MP, the measured current value Aa2 of the second motor pump MP, and the measured current value Aa2 of the third motor pump MP. The sum of the measured current values Aa3 (i.e., measured current value Ac) can be measured.

The control device 100 determines that the measured current value Aa1 is greater than the assumed current value (Aa1 > assumed current value), and the value obtained by subtracting the measured current value Aa1 from the measured current value Ab (i.e., Ab-Aa1) is greater than the assumed current value. When it is large ((Ab-Aa1) > assumed current value) and the value obtained by subtracting the measured current value Ab from the measured current value Ac (i.e. Ac-Ab, where Ab=Aa1+Aa2) is lower than the assumed current value. It is determined that an abnormality has occurred in the third motor pump MP. The value obtained by subtracting the measured current value Ab from the measured current value Ac corresponds to the assumed current value Aa3.

When the control device 100 determines that the measured current value Amax is lower than the lower limit current value and that no abnormality has occurred in the first motor pump MP, the second motor pump MP, and the third motor pump MP, It is determined that an error has occurred in the fourth motor pump MP. In addition, even when the pump unit PU is equipped with five or more motor pumps MP connected in series, the control device 100 determines the abnormality of each motor pump MP by a method similar to the method described above. You can.

In the above-described embodiment, the control method of the plurality of motor pumps MP connected in series has been described, but the pump unit PU may control the plurality of motor pumps MP connected in parallel. When controlling a plurality of motor pumps MP (see FIGS. 11 and 12) connected in parallel, the control device 100 may be configured to deviate the respective startup timings of the plurality of motor pumps MP.

By shifting the startup timing, the pump unit PU can form a swirling flow within the pipe 65. By forming a swirling flow, foreign matter and air adhering to the pipe 65 can be removed, and furthermore, retention of the liquid to be handled can be prevented.

In order to form a swirling flow, the control device 100 starts one of the plurality of motor pumps MP (i.e., the first motor pump MP) and then moves the motor pump MP adjacent to the started motor pump MP (i.e., the first motor pump MP). You may start the motor pump MP (second motor pump MP). In this way, by continuously starting the adjacent motor pump MP, the pump unit PU can form a swirling flow that rotates according to the starting order of the motor pump MP.

For example, when three motor pumps MP are arranged, the control device 100 may start the first motor pump MP and then start the second motor pump MP, or the third motor pump MP. After starting MP, the first motor pump MP adjacent to the third motor pump MP may be started.

23 is a diagram showing another embodiment of an impeller. In this embodiment, illustration of the bearing 5 is omitted. In the above-described embodiment, the impeller 1 is provided with an annular protrusion 17 extending from the outer edge 11a of the side plate 11 toward the suction portion 15 (see Fig. 1). In the embodiment shown in FIG. 23, the side plate 11 of the impeller 1 has an annular protrusion 117 disposed inside the outer edge 11a of the side plate 11 in the radial direction.

The rotor 2 is disposed at an annular step formed between the outer edge 11a of the side plate 11 and the protrusion 117, and the exposed portion of the rotor 2 is covered by the cover 110. . The cover 110 is one of the components of the motor pump MP. Examples of the cover 110 include a corrosion-resistant can, a resin coat, or a Ni plating coat.

In one embodiment, the iron core 2a of the rotor 2 is joined to the protruding portion 117 by means such as adhesive, press fitting, shrink fitting, or welding. Similarly, the cover 110 is joined to the impeller 1 by means such as adhesive, press fitting, shrink fitting, or welding.

Figure 24 is a diagram showing another embodiment of the impeller. In this embodiment, illustration of the bearing 5 is omitted. As shown in FIG. 24 , the impeller 1 may be provided with an annular mounting portion 118 disposed outside the protruding portion 117 in the radial direction. By inserting the rotor 2 into the annular space between the mounting portion 118 and the protruding portion 117, the rotor 2 can be more reliably fixed to the side plate 11. Also in this embodiment, the exposed portion of the rotor 2 is covered with the cover 110.

Fig. 25 is a view showing a seal member disposed between the cover and the side plate. In this embodiment, illustration of the bearing 5 is omitted. As shown in FIG. 25, a seal member (e.g., O-ring) is provided between the cover 110 and the side plate 11 (more specifically, the outer edge 11a and the protrusion 117 of the side plate 11). ) By arranging (120, 121), contact of the liquid with the rotor 2 can be reliably prevented.

The impeller 1 according to the embodiment shown in FIGS. 1 to 25 is manufactured by, for example, casting, stainless steel press molding, or resin molding. The impeller 1 according to the embodiment shown in FIGS. 26 to 34 described below may similarly be manufactured by means such as casting, stainless steel press molding, or resin molding.

Figure 26 is a diagram showing another embodiment of the impeller. In this embodiment, illustration of the bearing 5 is omitted. As shown in FIG. 26, the rotor 2 is connected to the outer edge of the side plate 11 so as to block the flow path (i.e., outlet flow path) of the impeller 1 formed between the main plate 10 and the side plate 11. It is fixed at (11a). Also in this embodiment, the rotor 2 is disposed in the suction side area Ra.

In the embodiment shown in FIG. 26, the rotor 2 is not covered with the cover 110, and the rotor 2 is made of a corrosion-resistant material. Even in the above-described embodiment, the rotor 2 does not necessarily need to be covered with the cover 110, and may be made of a corrosion-resistant material. In one embodiment, the rotor 2 may be covered with a cover 110.

With this configuration, the liquid passing through the outlet flow path collides with the inner peripheral surface of the rotor 2, and the direction of the liquid is changed. After that, the handling liquid is discharged from the discharge port 22a through the gap between the main plate 10 and the discharge casing 22.

23 to 26, since the rotor 2 and the bearing 5 are arranged in the suction side area Ra of the impeller 1, the motor pump MP has a compact structure. there is.

Fig. 27 is a diagram showing another embodiment of a motor pump. As shown in FIG. 27, the motor pump MP includes a first impeller 1A disposed on the suction port 21a side, a second impeller 1B disposed on the discharge port 22a side, and a first impeller 1A. ) and a communication shaft 126 connected to the second impeller 1B. The rotor 2 is fixed to the first impeller 1A, and the stator 3 is disposed outside the rotor 2 in the radial direction. The bearing 5 supports the first impeller 1A, and the second impeller 1B is supported by the bearing 5 via the communication shaft 126.

In the embodiment shown in FIG. 27, the motor pump MP is provided with an intermediate casing 125 disposed between the first impeller 1A and the second impeller 1B. The intermediate casing 125 is an annular partition that isolates the discharge side of the first impeller 1A from the suction side of the second impeller 1B. In this embodiment, the intermediate casing 125 is fixed to the stator casing 20.

In the embodiment shown in FIG. 27, the motor pump MP is provided with two impellers 1, but the number of impellers 1 is not limited to this embodiment. The motor pump MP may be provided with a plurality of intermediate casings 125 depending on the number of impellers 1. In other words, the motor pump MP may be provided with a plurality of impellers 1 including at least the first impeller 1A and the second impeller 1B.

Fig. 28 is a diagram showing another embodiment of a motor pump. As shown in FIG. 28, the motor pump MP rotatably supports the communication shaft 126 and further includes a discharge side bearing 128 disposed on the discharge side of the second impeller 1B. The discharge side bearing 128 is mounted on the discharge casing 22, and sealing members (e.g., O-rings) 127A and 127B are disposed in the gap between the discharge side bearing 128 and the discharge casing 22. It is done. Also, in the embodiment shown in FIG. 28, the motor pump MP is provided with two impellers 1, but the number of impellers 1 is not limited to this embodiment. The motor pump MP may be provided with a plurality of impellers 1, including at least the first impeller 1A and the second impeller 1B.

As shown in FIG. 28, the discharge casing 22 has a flow path 129 communicating with the discharge port 22a. The flow path 129 is arranged outside the communication shaft 126 in the radial direction. The handling liquid discharged from the second impeller 1B is discharged to the outside through the flow path 129 and the discharge port 22a.

In the embodiment shown in FIG. 28, the first impeller 1A and the second impeller 1B are supported not only by the bearing 5 but also by the discharge side bearing 128. The discharge side bearing 128 is a radial bearing. With this structure, the motor pump MP can suppress the displacement of the first impeller 1A and the second impeller 1B in the radial direction.

Fig. 29 is a diagram showing another embodiment of a motor pump. As shown in FIG. 29, the motor pump MP may be provided with a communication shaft 126 on which one impeller 1 is fixed, and a discharge side bearing 128 that rotatably supports the communication shaft 126. .

Figure 30 is a diagram showing a motor pump in which various components can be selected depending on operating conditions. In Figure 30, the horizontal axis represents the flow rate, and the vertical axis represents the head. As shown in FIG. 30, the motor pump MP is configured to enable selection of optimal components according to various operating conditions (i.e., size of flow rate and size of head).

In the embodiment shown in FIG. 30, the motor pump MP can be selected from a plurality of (four in this embodiment) different configurations depending on the size of the head and the size of the flow rate (see MPA to MPD in FIG. 30). . In this embodiment, the motor pump MP includes a plurality of impellers 1 having different sizes, a plurality of rotors 2 fixed to the plurality of impellers 1 and having different lengths, and a plurality of rotors. A plurality of stators (3) having a length corresponding to the length of the electrons (2), a plurality of stator casings ( 20) is provided.

The size of the motor capacity of the motor pump MP depends on the length Lg of the stator 3. The size of the head of the motor pump MP depends on the size of the diameter D1 of the impeller 1. The size of the flow rate of the motor pump MP depends on the size of the outlet flow path B2 of the impeller 1.

The plurality of impellers 1 are provided with a plurality of side plates 11 having the same diameter and a plurality of main plates 10 having different diameters. In this specification, the diameter D1 of the impeller 1 corresponds to the diameter of the main plate 10.

The relationship between motor pump MPA and motor pump MPB will be explained. As shown in Fig. 30, motor pump MPA and motor pump MPB have the same motor capacity (i.e., LgA = LgB). Motor pump MPA has a higher head capacity than motor pump MPB (i.e. D1A>D1B). Motor pump MPB has a higher flow capacity than motor pump MPA (i.e. B2B>B2A).

The relationship between motor pump MPA and motor pump MPC will be explained. Motor pump MPC has a larger motor capacity than motor pump MPA (i.e., LgC>LgA). The motor pump MPC has the same head capacity as the motor pump MPA (i.e. D1A=D1C). Motor pump MPC has a higher flow capacity than motor pump MPA (i.e. B2C>B2A).

The relationship between motor pump MPB and motor pump MPC will be explained. Motor pump MPC has a larger motor capacity than motor pump MPB (i.e., LgC>LgB). The motor pump MPC has a higher head capacity than the motor pump MPB (i.e. D1C>D1B). The outlet flow path B2B of the impeller 1 of the motor pump MPB is the same as the outlet flow path B2C of the impeller 1 of the motor pump MPC, or has a size larger than the outlet flow path B2C (i.e., B2B≥B2C).

The relationship between motor pump MPC and motor pump MPD will be explained. The motor pump MPC has the same motor capacity as the motor pump MPD (i.e. LgC=LgD). Motor pump MPC has a higher head capacity than motor pump MPD (i.e. D1C>D1D). Motor pump MPD has a higher flow capacity than motor pump MPC (i.e. B2D>B2C).

The relationship between motor pump MPB and motor pump MPD will be explained. Motor pump MPD has a larger motor capacity than motor pump MPB (i.e., LgD>LgB). Motor pump MPD has a higher flow capacity than motor pump MPB (i.e. B2D>B2B). Motor pump MPB has the same head capacity as motor pump MPD (i.e. D1B=D1D).

As shown in FIG. 30, in all motor pumps MP, the inner diameter D2 and outer diameter D3 of the stator casing 20 are the same. Accordingly, the operator can prepare component parts having different sizes according to head capacity and flow capacity, and select the optimal component part from a plurality of component parts based on the operating conditions of the motor pump MP.

By making the inner diameter D2 and the outer diameter D3 of the stator casing 20 the same, the component parts (e.g., bearing 5, suction casing 21, and discharge casing 22) that do not depend on head capacity or flow capacity. The performance of the pump unit PU can be easily changed without changing the size.

FIG. 31A is a cross-sectional view of a motor pump according to another embodiment, and FIG. 31B is a view of the motor pump shown in FIG. 31A when viewed from the axial direction. As shown in FIGS. 31A and 31B, the motor pump MP may be provided with a turning prevention portion (in other words, fail stop) 130 disposed on the rear side of the impeller 1.

In the embodiment shown in FIG. 31B, one anti-swing portion 130 is disposed, but at least one anti-spin portion 130 may be disposed. The rotation prevention portion 130 is fixed to the discharge casing 22 and faces the main plate 10 of the impeller 1. The turning prevention unit 130 can prevent the handling liquid discharged from the impeller 1 from turning between the impeller 1 and the discharge casing 22.

FIG. 32A is a cross-sectional view of a motor pump according to another embodiment, and FIG. 32B is a front view of the suction casing of the motor pump shown in FIG. 32A. As shown in FIGS. 32A and 32B, the motor pump MP is provided with a suction casing 141 and a discharge casing 142 having a flat flange shape.

In the above-described embodiment, the suction port 21a of the suction casing 21 protrudes from the outer surface of the suction casing 21, and similarly, the discharge port 22a of the discharge casing 22 is of the discharge casing 22. It protrudes from the outside. In this embodiment, since the suction casing 141 has a flat flange shape, the suction port 141a is formed on the same plane as the outer surface of the suction casing 141. Similarly, since the discharge casing 142 has a flat flange shape, the discharge port 142a is formed on the same plane as the outer surface of the discharge casing 142.

With this structure, the connection pipe 140 connected to the motor pump MP can be directly connected to the suction casing 141. Although not shown, the connection pipe 140 may be directly connected to the discharge casing 142 having a flat flange shape.

With this configuration, there is no need to arrange a member (connection member) connecting the connection pipe 140 and the suction casing 141, thereby reducing the number of parts for connecting the pipe (not shown) to the motor pump MP. You can.

Since the connecting member is a member from which leakage of liquid is expected, leakage of liquid can be reliably prevented by excluding the connecting member. In this embodiment, although not shown, a sealing member (for example, an O-ring or a gasket) is disposed between the connection pipe 140 and the suction casing 141.

On the radial outer side of the suction port 141a of the suction casing 141, an insertion hole 141b is formed into which a fastener 150 for fastening the connection pipe 140 and the suction casing 141 is inserted. The connection pipe 140 has a through hole 140a communicating with the insertion hole 141b. The operator can fasten the connection pipe 140 and the suction casing 141 to each other by inserting the fastener 150 into the through hole 140a and the insertion hole 141b.

On the radial outer side of the discharge port 142a of the discharge casing 142, a bolt accommodating portion 142b is formed to accommodate the head portion 25a of the through bolt 25. By accommodating the head portion 25a of the through bolt 25 in the bolt accommodation portion 142b, the head portion 25a can be prevented from protruding from the discharge casing 22.

In one embodiment, the suction casing 141 may have a bolt accommodating portion corresponding to the bolt accommodating portion 142b. That is, at least one of the suction casing 141 and the discharge casing 142 has a bolt accommodating portion that accommodates the head portion 25a of the through bolt 25.

Figure 33 is a diagram showing a pump unit including a motor pump connected in series. As shown in Figure 33, the motor pump MP shown in Figures 32a and 32b is provided with a suction casing 141 and a discharge casing 142 having a flat flange shape, so the suction casings are arranged adjacent to each other. (141) and the discharge casing (142) can be in surface contact with each other. The suction casing 141 and the discharge casing 142, which are in surface contact with each other, correspond to the intermediate casing.

Although not shown, a sealing member (for example, an O-ring or a gasket) is disposed between the suction casing 141 and the discharge casing 142, which are in surface contact with each other.

According to this embodiment, there is no need to arrange the intermediate casing 61 (see FIG. 10), and a plurality of motor pumps MP having the same structure can be connected directly in series by a simple operation. A pump unit PU including an MP can be configured.

The motor pump MP according to this embodiment has simple main components (namely, the impeller 1, the rotor 2, the stator 3, and the bearing 5), and is compact and lightweight. there is. Therefore, by using the through bolt 25, a plurality of motor pumps MP arranged in series can be easily and integrally fastened.

Additionally, by bringing the suction casing 141 and the discharge casing 142 into surface contact with each other, the thermal conductivity of the pump unit PU can be improved, and temperature balance between the plurality of motor pumps MP can be achieved. As a result, the pump unit PU can operate stably.

Figure 34 is a diagram showing another embodiment of the impeller. In the above-described embodiment, the impeller 1 is a centrifugal impeller. More specifically, the impeller 1 is provided with a main plate 10 extending perpendicular to the direction of the center line CL, and the liquid pressurized by the impeller 1 is discharged perpendicular to the center line CL. In the embodiment shown in FIG. 34, the impeller 1 is a four-flow impeller. More specifically, the impeller 1 is provided with a main plate 160 inclined at a predetermined angle with respect to the center line CL direction. The main plate 160 is inclined from the suction side toward the discharge side, and the liquid pressurized by the impeller 1 is discharged in an inclined direction outward with respect to the center line CL.

Fig. 35 is a diagram showing another embodiment of a motor pump. As shown in FIG. 35, the motor pump MP is provided with a rotor holder 200 that holds the rotor 2 and an impeller 1 that is a press molded product to which the rotor holder 200 is fixed. there is. Also in this embodiment, the rotor 2 and bearing 5 are arranged in the suction side area of the impeller 1 (see FIG. 1).

The impeller 1 is provided with a main plate 10, a side plate 11, and a plurality of blades 12, and each of these main plate 10, side plates 11, and blades 12 has a lead plate 10, a side plate 11, and a plurality of blades 12. It is a press-molded product made of metal material with excellent malleability. An example of such a metal material is stainless steel. In one embodiment, these main plates 10, side plates 11, and wings 12 are press molded separately and joined after molding.

By configuring the impeller 1 as a press-molded product, the overall weight of the impeller 1 can be realized. Such reduction in weight of the impeller 1 contributes to reducing (or eliminating the need for) balance (dynamic balance) adjustment to determine the position of the center of gravity of the impeller 1 to a desired position. Additionally, with this configuration, the distance between the main plate 10 and the side plate 11 can be reduced, and as a result, further compactization of the motor pump MP can be realized.

The rotor holder 200 prevents corrosion of the rotor 2 due to contact of the rotor 2 with the handling liquid. The rotor holder 200 includes a press-formed annular accommodating portion 201 that accommodates the rotor 2, and an annular closing plate 202 that closes the accommodating portion 201. The receiving portion 201 has an annular concave shape and is arranged concentrically with the impeller 1 with the center line CL as the center. For example, the receiving portion 201 may be manufactured by deep drawing molding.

The receiving portion 201 is fixed (joined) to the side plate 11 of the impeller 1. In one embodiment, the accommodation portion 201 is welded to the side plate 11. In order to easily fix the accommodating part 201 to the impeller 1, the impeller 1 and the accommodating part 201 are preferably made of the same material.

Figure 36 is an enlarged view of the rotor holder. As shown in FIG. 36, in order to prevent the handling liquid from entering from the gap between the accommodating part 201 and the blocking plate 202, the rotor holder 200 includes the accommodating part 201 and the blocking plate ( 202) and has a seal member (eg, O-ring) 205 disposed between them. The seal member 205 fixes the blocking plate 202 to the receiving portion 201 by its elastic force.

In one embodiment, the blocking plate 202 may be inserted into the rotor holder 200 by a mechanical insertion method. An example of a mechanical insertion method is press-fitting of the closure plate 202 into the rotor holder 200. As another example of a mechanical insertion method, after heating the rotor holder 200, the blocking plate 202 may be inserted into the thermally expanded rotor holder 200 (shrink fit). In this case, in order to reduce the thermal effect (i.e., thermal demagnetization) on the magnetic force of the rotor 2, after inserting the blocking plate 202 into the rotor holder 200, the rotor 2 is magnetized. It is desirable. As another example of a mechanical insertion method, the closure plate 202 may be inserted into the rotor holder 200 by cold fitting. As another example of a mechanical insertion method, the blocking plate 202 may be inserted into the rotor holder 200 using an adhesive.

The receiving portion 201 of the rotor holder 200 includes an outer annular portion 231, an inner annular portion 232 disposed radially inside the outer annular portion 231, an outer annular portion 231, and It is provided with an annular back part 233 connecting the inner annular part 232.

The rotating side bearing body 6 is mounted on the rotor holder 200, and the fixed side bearing body 7 is disposed on the suction side of the rotating side bearing body 6 (see Fig. 35). Seal members 31A and 31B are disposed between the inner annular portion 232 and the cylindrical portion 6a of the rotation side bearing body 6. In this embodiment, two sealing members are disposed, but the number of sealing members is not limited to this embodiment.

In order to bring the seal members 31A and 31B into close contact with the inner annular portion 232, the inner annular portion 232 is processed smoothly in the press forming process of the rotor holder 200. In this way, by going through the press molding process, a new additional process for bringing the seal members 31A and 31B into close contact with the inner annular portion 232 can be omitted.

The receiving portion 201 (more specifically, the outer annular portion 231 and the inner annular portion 232) extends in parallel with the cylindrical portion 6a of the rotation side bearing body 6, and the cylindrical portion 6a ) is disposed on the radial inner side of the inner annular portion 232 of the rotor holder 200. The flange portion 6b of the rotation side bearing body 6 extends in parallel with the blocking plate 202 and is disposed adjacent to the blocking plate 202.

If air exists inside the accommodating part 201, there is a risk that the closure plate 202 may move in a direction away from the accommodating part 201 due to expansion of the air in the accommodating part 201. In this embodiment, the flange portion 6b of the rotation-side bearing body 6 adjacent to the blocking plate 202 can restrict the movement of the blocking plate 202.

In one embodiment, in order to reduce the amount of air expansion in the accommodating part 201, the rotor holder 200 uses filler (e.g., grease, potting material, adhesive, etc.) filled in the accommodating part 201. You may prepare it.

The receiving portion 201 has an outer surface 201a in contact with the rotation side bearing body 6, an inner surface 201b in contact with the rotor 2, and a corner surface 201c formed at a corner of the inner surface 201b. has. As described above, since the rotor holder 200 is a press-molded product, each surface 201c is a smooth curved surface. On the other hand, since the rotor 2 is manufactured by laminating laminated cores that are punched products of iron plates, the rotor 2 has sharp corners.

Therefore, even if the rotor 2 is inserted into the housing portion 201, the sharp corners of the rotor 2 come into contact with the smooth face 201c, and the entire rotor 2 is in close contact with the back portion 233. Can not. As a result, the operator cannot reliably position the rotor 2 with respect to the rotor holder 200, and there is a risk that the rotor 2 cannot be stably accommodated in the rotor holder 200. .

Accordingly, the rotor holder 200 includes a spacer 203 disposed between the receiving portion 201 and the rotor 2. In the embodiment shown in FIG. 36, the spacer 203 is a shim disposed between the rear portion 233 and the rotor 2. By disposing the spacer 203, contact of the rotor 2 with each surface 201c can be prevented. As a result, the rotor 2 is in close contact with the spacer 203 and is accommodated in the rotor holder 200, so the operator can reliably position the rotor 2 with respect to the rotor holder 200. You can. With this configuration, the operator can stably accommodate the rotor 2 in the rotor holder 200.

Fig. 37 is a diagram showing another embodiment of a spacer. As shown in FIG. 37, the rotor holder 200 may be provided with a spacer 210 disposed between the accommodating portion 201 and the rotor 2. In the embodiment shown in FIG. 37, the spacer 210 is a protrusion protruding from the rear portion 233 of the rotor holder 200.

Methods of fastening the rotor 2 to the rotor holder 200 include, for example, a fastening method using an adhesive, a fastening method by shrink fitting, and a fastening method by cold fitting. When a fastening method that involves a change in temperature of the rotor 2 and/or the rotor holder 200 (for example, shrink fitting, cooling fitting, etc.) is adopted, the rotor 2 and the rotor holder 200 It is necessary to determine the dimensions of (200) appropriately. Therefore, as a simple fastening method, it is desirable to adopt a fastening method at room temperature.

Fig. 38 is a diagram showing a rotor inserted into a rotor holder. As shown in FIG. 38, the inner surface 230 of the rotor 2 in contact with the inner annular portion 232 has a polygonal shape (in this embodiment, an octagon). Since the inner surface 230 of the rotor 2 has a polygonal shape, when the rotor 2 is inserted into the rotor holder 200 at room temperature, the inner annular portion 232 of the rotor holder 200 ) may be in line contact with the inner surface 230 of the rotor 2.

Such contact can prevent the entire rotor 2 from contacting the inner annular portion 232 of the rotor holder 200. Therefore, even if the rotor 2 is press-fitted into the rotor holder 200, the contact area of the rotor 2 with the rotor holder 200 can be reduced, and as a result, the rotor holder 200 is deformed. can be prevented.

Figure 39 is a diagram showing a rotor inserted into a rotor holder. As shown in FIG. 39, the inner annular portion 232 may have a plurality of protrusions 235 formed at a contact portion with the rotor 2. The protrusion 235 of the inner annular portion 232 faces the inner surface 230 of the rotor 2, and the rotor 2 is in contact with the protrusion 235. Even with this configuration, the contact area of the rotor 2 with the rotor holder 200 can be reduced, and as a result, deformation of the rotor holder 200 can be prevented.

Returning to Fig. 35, the motor pump MP accommodates the stator 3 and is provided with a stator casing 20 that is integrally molded with a resin mold with the stator 3. As shown in FIG. 35, the stator 3 includes a stator core 3a and a coil 3b wound around the stator core 3a through an insulating material 220. Examples of the insulating material 220 include insulating paper and resin. The resin constituting the stator casing 20 is made of a material (same material as the potting material) that has insulation and excellent thermal conductivity.

The motor pump MP has a motor frame 221 that covers the outer peripheral surface of the stator casing 20 and is in contact with the stator 3. The motor frame 221 has a through hole 242 through which the power line 105 and signal line 106 extending from the coil 3b pass. The motor frame 221 is made of a material with excellent thermal conductivity (for example, a metal material). In this way, the stator 3 is covered with the stator casing 20, which has excellent thermal conductivity, and is in contact with the motor frame 221, which has excellent thermal conductivity. Accordingly, the heat emitted from the coil 3b of the stator 3 is discharged to the outside through the stator casing 20 and the motor frame 221.

A sealing member (for example, an O-ring) 241 is disposed between the suction casing 21 and discharge casing 22 and the stator casing 20 to prevent leakage of the handling liquid to the outside. The stator casing 20 has a seal groove 229 into which the seal member 241 is mounted.

The stator casing 20 is molded by pouring resin into a mold. By forming a protrusion corresponding to the seal groove 229 in advance on the mold, the process of newly forming the seal groove 229 after manufacturing the stator casing 20 can be omitted. In one embodiment, a seal groove (not shown) into which the seal member 241 is mounted may be formed in the suction casing 21 and the discharge casing 22.

In this embodiment, the stator casing 20, the return blade 30, and the partition plate 240 fixed to the return blade 30 are integrally molded members manufactured by resin mold molding. The return blade 30 may have a unique non-linear shape as a flow path. According to this embodiment, by employing resin mold molding in which resin is poured into a mold, the stator casing 20, the return blade 30, and the partition plate 240 can be manufactured integrally and easily in large quantities. .

In one embodiment, in order to improve heat dissipation from the coil 3b, the stator casing 20 may cover the stator core 3a and the coil 3b covered with the potting material. In this way, by covering the coil 3b with a potting material, the potting material enters between the wires constituting the coil 3b, and thus the heat dissipation property of the coil 3b can be improved. In this state, the heat dissipation of the stator 3 can be further improved by covering the stator core 3a and the coil 3b with the resin constituting the stator casing 20.

As an example of the resin constituting the stator casing 20, a two-liquid mixed-curing type resin (e.g., dicyclopentadiene resin) or a heat-curing type resin (e.g., epoxy resin) with excellent fluidity at room temperature is used. I can hear it. In one embodiment, the strength of the stator casing 20 can be improved by mixing fiber as an additive into the resin. In one embodiment, the thermal conductivity of the stator casing 20 can be improved by mixing a material with high thermal conductivity as an additive. Both of these fibers and highly thermally conductive materials may be mixed into the resin constituting the stator casing 20 as additives.

Figure 40 is a diagram showing another embodiment of an impeller. As shown in FIG. 40, the motor pump MP is equipped with an impeller 1, which is a resin molded product in which the rotor holder 200 is integrally molded. The impeller 1 is made of resin in which the main plate 10, side plates 11, and blades 12 are integrally molded. In one embodiment, the strength of the impeller 1 can be improved by mixing fiber as an additive into the resin.

The rotor holder 200 includes an annular accommodating part 251 formed by a resin mold that accommodates the rotor 2, and a ring holder 252 that closes the accommodating part 251. The impeller 1 and the receiving portion 251 of the rotor holder 200 are made of resin molded integrally.

The ring holder 252 is made of a press-formed corrosion-resistant material (for example, stainless steel). The ring holder 252 and the rotor 2 are fastened by mechanical methods such as shrink fitting, cold fitting, or press fitting. In one embodiment, the ring holder 252 and the rotor 2 may be fastened with an adhesive.

When fastening the rotor 2 to the ring holder 252, in order to reduce the indentation load of the rotor 2, the inner surface 230 of the rotor 2 in contact with the ring holder 252 is polygonal. It may have a shape (see FIG. 38), and the ring holder 252 may have a plurality of protrusions 235 formed at the contact portion with the rotor 2 (see FIG. 39).

Figure 41 is an enlarged view of the rotor holder. As shown in FIG. 41, the ring holder 252 is provided with a ring portion 253 having an L-shaped cross-sectional shape and a bent portion 254 bent from the ring portion 253. The ring portion 253 of the ring holder 252, which is a press-molded product, has a smooth face 257 formed at its bent portion.

Also in this embodiment, the rotor 2 and bearing 5 are arranged in the suction side area of the impeller 1 (see FIG. 1). The rotation side bearing body 6 is mounted on the ring holder 252, and the fixed side bearing body 7 is disposed on the suction side of the rotation side bearing body 6. The seal members 31A and 31B are disposed between the ring portion 253 of the ring holder 252 and the cylindrical portion 6a of the rotation side bearing body 6. In this embodiment as well, since the ring portion 253 is press formed, a new additional process for bringing the seal members 31A and 31B into close contact with the ring portion 253 can be omitted.

As described above, the rotor 2 has sharp corners. Therefore, even if the rotor 2 is mounted on the ring holder 252, the sharp corners of the rotor 2 come into contact with the smooth face 257, and as a result, the operator places the rotor 2 on the ring holder 252. There is a risk that it may not be stably accommodated in the holder 200.

Accordingly, the rotor holder 200 includes a spacer 260 disposed between the ring holder 252 and the rotor 2. In the embodiment shown in FIG. 41, the spacer 260 is a shim disposed between the ring holder 252 and the rotor 2. In one embodiment, the spacer 260 may be a protrusion (not shown) protruding from the ring holder 252 (see Fig. 37).

When manufacturing the rotor holder 200, resin is poured into the mold with the ring holder 252 and the rotor 2 mounted on the ring holder 252 set in the mold. By this manufacturing method, the resin constituting the accommodating portion 251 of the rotor holder 200 surrounds the rotor 2, and as a result, the accommodating portion 251 seals the rotor 2. do.

The resin flowing into the mold is high temperature. Therefore, when the rotor 2 mounted on the ring holder 252 is brought into contact with high-temperature resin, the rotor 2 becomes thermally demagnetized. Therefore, after manufacturing the rotor holder 200, it is necessary to magnetize the rotor 2.

In this embodiment, the housing portion 251 of the rotor holder 200 and the impeller 1 are integrally molded members manufactured by resin mold molding. The impeller 1, like the return blade 30, may have a unique non-linear shape as a flow path. According to this embodiment, by employing resin mold molding in which resin is introduced into a mold, the accommodating portion 251 and the impeller 1 of the rotor holder 200 can be manufactured integrally and easily in large quantities.

The ring holder 252 has a rotation prevention structure formed at a connection portion with the receiving portion 251. By operating the motor pump MP, the rotational torque of the rotor 2 is transmitted to the impeller 1. Since the ring holder 252 has a rotation prevention structure, even if the impeller 1 rotates, the ring holder 252 does not rotate relative to the receiving portion 251. Hereinafter, the specific configuration of the rotation prevention structure will be described.

As shown in FIG. 41, the housing portion 251 includes a main body portion 255 that surrounds most of the rotor 2, and a bent portion 256 bent from the main body portion 255. The ring portion 253 of the ring holder 252 has an embedded hole 253a in which a portion of the receiving portion 251 (more specifically, the bent portion 256) is embedded. A plurality of these embedded holes 253a are formed along the circumferential direction of the ring holder 252.

By embedding part of the bent portion 256 in the embedding hole 253a, the ring holder 252 and the receiving portion 251 are firmly fastened to each other. This embedding is performed by pouring resin into a mold during manufacturing of the rotor holder 200.

Similarly, the bent portion 254 of the ring holder 252 has an embedded hole 254a in which a portion of the main body portion 255 of the receiving portion 251 is embedded. A plurality of these embedded holes 254a are formed along the circumferential direction of the ring holder 252. By embedding part of the main body portion 255 in the embedding hole 254a, the ring holder 252 and the receiving portion 251 are firmly fastened to each other. This embedding is performed by pouring resin into a mold during manufacturing of the rotor holder 200. According to this embodiment, separation of the rotor holder 200 from the rotor 2 due to the difference in linear expansion of the rotor 2 and the rotor holder 200 due to temperature changes can be mechanically suppressed. You can.

Figure 42 is a diagram showing another embodiment of the rotation prevention structure. As shown in Fig. 42, the anti-rotation structure may be bent portions 253b and 254b that are bent in the shape of the Japanese letter コ. More specifically, the ring portion 253 of the ring holder 252 has a bent portion 253b that is bent in the shape of the Japanese letter コ, and similarly, the bent portion 254 is bent in the shape of the Japanese letter コ. It has wealth (254b). Even with this structure, the ring holder 252 and the receiving portion 251 are firmly fastened to each other. Additionally, the embodiment shown in FIG. 41 and the embodiment shown in FIG. 42 may be combined.

In one embodiment, the rotation prevention structure may be a cutting groove (not shown) on a gear formed in each of the ring portion 253 and the bent portion 254. A plurality of these cutting grooves are formed along the circumferential direction of the ring holder 252.

In one embodiment, in order to improve the adhesion between the receiving portion 251 and the ring holder 252, a primer is applied to the surface of the ring holder 252 in advance to remove oxides on the surface of the ring holder 252. Processing may be performed.

Also in the embodiments shown in FIGS. 40 to 42, the stator casing 20 has a structure similar to that of the stator casing 20 in the embodiments shown in FIGS. 35 to 39. More specifically, the motor pump MP includes a stator casing 20 that accommodates the stator 3 and is integrally molded with a resin mold, and covers the outer peripheral surface of the stator casing 20, and further includes a stator casing 20 that is integrally molded with a resin mold. It is provided with a motor frame 221 in contact with (3).

Figure 43 is a diagram showing another embodiment of a motor pump. In this embodiment, components that are the same or equivalent to those in the above-described embodiment are given the same reference numerals and redundant descriptions are omitted.

As shown in FIG. 43, the motor pump MP includes at least a first impeller 1A disposed on the suction port 21a side and a second impeller 1B disposed on the discharge port 22a side. It is provided with an impeller (1). In one embodiment, at least one impeller 1 may be disposed between the first impeller 1A and the second impeller 1B. The rotor holder 200 holding the rotor 2 is fixed to the first impeller 1A, and on the radial outer side of the rotor 2, a stator ( 3) is placed.

As shown in FIG. 43, since the rotor 2 accommodated in the rotor holder 200 is fixed to the first impeller 1A, the rotational force of the rotor 2 is generated by the first impeller 1A. It acts on. The rotational force acting on the first impeller 1A is transmitted to the second impeller 1B through the communication shaft 270. In this way, since the first impeller 1A receives all of the rotational force of the rotor 2, the load acting on the first impeller 1A increases, and there is a risk that the first impeller 1A may be damaged.

Therefore, the first impeller 1A preferably has a higher strength than the other impeller 1 (in this embodiment, the second impeller 1B). In addition, in order to realize the high head of the motor pump MP according to this embodiment, it is preferable that the first impeller 1A has high strength. In this way, it is desirable that the motor pump MP having a plurality of impellers 1 not only has a compact structure but also has a structure having high strength. With this structure, the motor pump MP can operate stably.

Therefore, the motor pump MP according to this embodiment not only has a compact structure, but also has a structure that can be operated stably. Hereinafter, the structure of the motor pump MP will be described with reference to the drawings.

The first impeller 1A is supported by the first bearing 5, and a communication shaft 270 is connected to the first impeller 1A. The second impeller 1B is connected to the communication shaft 270. The motor pump MP is provided with an intermediate casing 275 disposed between the first impeller 1A and the second impeller 1B, and a liner ring 276 is connected to the intermediate casing 275. The liner ring 276 is a ring member that suppresses backflow of the handling liquid sucked into the second impeller 1B.

In the embodiment shown in FIG. 43, the intermediate casing 275 is composed of a separate member from the stator casing 20, but the intermediate casing 275 and the stator casing 20 may be composed of the same member. . In this embodiment, the return blade 30 fixed to the intermediate casing 275 also serves as a guide blade that guides the handling liquid discharged from the first impeller 1A to the second impeller 1B. The return blade (and guide blade) 30 efficiently converts the flow rate of the handling liquid generated by the centrifugal force of the first impeller 1A into pressure and guides it to the liquid inlet of the first impeller 1B. can do.

The discharge casing 22 integrally constitutes a return blade 30 and a partition plate 245 fixed to the return blade 30. That is, the discharge casing 22, the return blade 30, and the partition plate 245 are integrally molded members. The discharge casing 22, the return blade 30, and the partition plate 245 formed as an integral part may be formed integrally by resin molding. In one embodiment, the discharge casing 22, the return blade 30, and the partition plate 245 may be separate members. The return blade 30 fixed to the discharge casing 22 also plays the same role as the return blade 30 fixed to the intermediate casing 275.

Figure 44 is a diagram showing another embodiment of a motor pump. In the embodiment shown in FIG. 43, the rotor holder 200 has the same structure as the rotor holder 200 according to the embodiment shown in FIG. 35. As shown in FIG. 44, the rotor holder 200 may have a structure similar to the rotor holder 200 according to the embodiment shown in FIG. 40.

Figure 45 is an enlarged view of the first impeller and the second impeller. As shown in FIG. 45, the boss portion 281 of the first impeller 1A has a larger size than the boss portion 282 of the second impeller 1B. The boss portion 281 is a connection portion with the communication shaft 270 of the first impeller 1A, and the boss portion 282 is a connection portion with the communication shaft 270 of the second impeller 1B.

In the embodiment shown in FIG. 45, the length L1 of the boss portion 281 in the center line CL direction is longer than the length L2 of the boss portion 282 in the center line CL direction. As described above, the load acting on the first impeller 1A as the rotor 2 rotates is greater than the load acting on the second impeller 1B. According to this embodiment, the boss portion 281 of the first impeller 1A has a larger size than the boss portion 282 of the second impeller 1B, so the first impeller 1A has a rotor It can sufficiently receive the rotational force of (2). As a result, the motor pump MP can prevent damage to the first impeller 1A.

As shown in FIG. 45, the motor pump MP is provided with a sleeve 280 that forms a predetermined distance between the first impeller 1A and the second impeller 1B. The sleeve 280 is disposed between the first impeller 1A and the second impeller 1B. By arranging the sleeve 280, the operator can easily manage the distance between the first impeller 1A and the second impeller 1B.

Each of the first impeller 1A and the second impeller 1B has a power transmission structure (key structure, two-chamfer structure, spline structure, etc.), and is connected to the communication shaft 270 by this structure. .

In this embodiment, each of the first impeller 1A and the second impeller 1B is connected to the communication shaft 270 by a fastener (for example, a nut) 273 fastened to the communication shaft 270. It is fixed. Between the first impeller 1A and the second impeller 1B, a sleeve 280 is disposed, and between the fastener 273 and the second impeller 1B, a rotation side bearing body 272 (described later) ) is placed.

Therefore, by fastening the fastener 273, the sleeve 280 is pressed into contact with the first impeller 1A, and the rotation side bearing body 272 is pressed into contact with the second impeller 1B. As a result, the first impeller 1A is sandwiched between the distal end 270a of the communication shaft 270 and the sleeve 280, and the second impeller 1B is between the sleeve 280 and the rotation side bearing body 272. ) is sandwiched between. In this way, the first impeller 1A and the second impeller 1B are firmly fixed to the communication shaft 270.

In this embodiment, the distal end 270a of the communication shaft 270 is disposed on the suction side, and the fastener 273 is disposed on the discharge side. In one embodiment, the tip portion 270a of the communication shaft 270 may have a hexagonal head or a hexagonal hole. With this structure, the worker can firmly fasten the fastener 273 to the communication shaft 270 while fixing the distal end 270a.

Fig. 46 is a diagram showing another embodiment of the connection structure between the first impeller and the second impeller and the communication shaft. As shown in FIG. 46, the motor pump MP is provided with collets 285 and 286 for fastening each of the first impeller 1A and the second impeller 1B to the communication shaft 270. Since the collets 285 and 286 have the same structure, the structure of the collet 285 will be described below.

The collet 285 is a cylindrical member having a tapered shape, and has a notch (not shown) extending in the direction of the center line CL. By inserting the collet 285 into the first impeller 1A from the rear side of the first impeller 1A, the collet 285 is dug into the first impeller 1A, and the first impeller 1A is connected to the communication shaft ( 270). Similarly, by inserting the collet 286 into the second impeller 1B, the collet 286 is dug into the second impeller 1B, and the second impeller 1B is fastened to the communication shaft 270. With this structure, each of the first impeller 1A and the second impeller 1B is more firmly fastened to the communication shaft 270.

When the first impeller 1A is fastened to the communication shaft 270, a gap is formed between the tip portion of the collet 285 and the tip portion 270a of the communication shaft 270. When the second impeller 1B is fastened to the communication shaft 270, a gap is formed between the tip of the collet 286 and the sleeve 280.

Returning to Figure 43 (and Figure 44), the motor pump MP includes a second bearing (plain bearing) 277 that rotatably supports the communication shaft 270, which is disposed at the rear end of the second impeller 1B. It is available. The second bearing 277 includes a rotating bearing body 272 disposed on the communication shaft 270 side and a fixed bearing body 271 disposed on the discharge casing 22 side.

The rotating side bearing body 272 is a rotating side cylindrical body mounted on the communicating shaft 270, and the fixed side bearing body 271 is installed in the discharge casing 22 and is also a rotating side bearing as a rotating side cylindrical body. It is a fixed-side cylindrical body surrounding the sieve 272. The partition plate 245 of the discharge casing 22 has a bearing support portion 246 that supports the fixed side bearing body 271. The fixed side bearing body 271 is fixed to the bearing support portion 246. A slight gap is formed between the fixed side bearing body 271 and the rotating side bearing body 272.

Examples of the material of the second bearing 277 include ceramic or resin. When the communication shaft 270 rotates with the rotation of the first impeller 1A, liquid enters between the fixed side bearing body 271 and the rotating side bearing body 272, and the fixed side bearing body 271, The rotation side bearing body 272 is supported by the dynamic pressure of this liquid.

By disposing the second bearing 277, the communicating shaft 270 is supported not only by the first bearing 5 fixed to the first impeller 1A but also by the second bearing 277. The communication shaft 270 to which the plurality of impellers 1 are connected has a length in the direction of the center line CL. The motor pump MP equipped with the first bearing 5 and the second bearing 277 suppresses axial shaking of the communication shaft 270 accompanying the lengthening of the communication shaft 270, and as a result, can be operated stably. You can.

The assembly procedure for the motor pump MP will be described. First, the first impeller 1A and the communication shaft 270 are fastened (process 1). After that, the intermediate casing 275 (see FIGS. 43 and 44) is inserted into the communication shaft 270 (Step 2), and the sleeve 280 is inserted into the communication shaft 270 (Step 3). Next, the second impeller 1B is inserted into the communication shaft 270, and the second impeller 1B and the communication shaft 270 are fastened (step 4). After that, the rotation side bearing body 272 is inserted into the communication shaft 270 (Step 5), and the discharge casing 22 is fastened to the stator casing 20 (Step 6). Afterwards, the fastener 273 is fastened to the communication shaft 270 (Step 7).

In one embodiment, the operator may perform step 5, then step 7, and then step 6. However, as the number of impellers 1 fixed to the communication shaft 270 increases, the communication shaft 270 becomes tilted, and as a result, there is a risk that the position of the communication shaft 270 may deviate from the center line CL direction.

Therefore, the worker installs the discharge casing 22, checks the positional relationship between the rotating bearing body 272 and the fixed bearing body 271, and fastens the fastener 273 to the communicating shaft 270. It is desirable. According to this embodiment, since the motor pump MP is a straight motor pump in which the suction port 21a and the discharge port 22a are arranged in a straight line, the communication shaft 270 is supported by the second bearing 277, The fastener 273 can be fastened to the communication shaft 270.

Figure 47 is a diagram showing another embodiment of a fastener. As shown in Figure 47, the fastener 290 has a smaller diameter than the rotation side bearing body 272. In one embodiment, the fastener 290 may have the same diameter as the rotation-side bearing body 272. A spacer 291 is disposed between the fastener 290 and the communication shaft 270. By inserting the fastener 290 into the screw hole 270b formed at the end of the communication shaft 270, the spacer 291 brings the rotation-side bearing body 272 into pressing contact with the second impeller 1B. According to this embodiment, even if the fixed-side bearing body 271 is inserted, contact of the fastener 290 with the fixed-side bearing body 271 is reliably prevented.

In this embodiment, by inserting each of the collets 285 and 286 into each of the first impeller 1A and the second impeller 1B, the first impeller 1A and the second impeller 1B are connected to the communication shaft ( 270) is sufficiently fastened. Therefore, the fastener 290 need only have a fastening force sufficient to limit the movement of the rotation side bearing body 272 in the center line CL direction.

Figure 48 is a diagram showing another embodiment of the second bearing. As shown in FIG. 48, the rotation-side bearing body 272 may be formed integrally with the communication shaft 270. In this case, the communication shaft 270 is made of the same bearing material as the rotation side bearing body 272 (for example, ceramic, steel, etc.). In the embodiment shown in FIG. 48, the fixed side bearing body 271 is arranged around the communicating shaft 270 formed integrally with the rotating side bearing body 272.

Fig. 49 is a diagram showing another embodiment of the second bearing. In the embodiment shown in FIG. 49, the fixed side bearing body 271 is formed integrally with the bearing support portion 246 of the discharge casing 22. In this embodiment, the bearing support portion 246 is made of the same bearing material (for example, ceramic, steel, resin, etc.) as the fixed side bearing body 271.

In this way, the motor pump MP may be provided with the first impeller 1A having the same structure as the impeller 1 according to the embodiment shown in FIGS. 35 to 39, or the embodiment shown in FIGS. 40 to 42. A first impeller 1A having the same structure as the impeller 1 in terms of shape may be provided. In one embodiment, the motor pump MP may be provided with a first impeller 1A having the same structure as the impeller 1 according to the embodiment shown in FIGS. 1 to 34. In other words, the embodiments shown in FIGS. 1 to 49 may be combined as much as possible.

Fig. 50 is a diagram showing a side plate provided in the motor pump according to the above-described embodiment. As shown in FIG. 50, the motor pump MP may further be provided with a side plate 300 that restricts the outflow of the liquid (handled liquid) pressurized by the impeller 1 to the discharge casing 22. In the embodiment shown in Figure 50, the side plate 300 has a disk shape and is fixed to the return blade 30.

The side plate 300 is disposed between the main plate 10 and the return blade 30 of the impeller 1. A part of the liquid pressurized by the impeller 1 is discharged from the discharge port 22a through the return blade 30 and the gap between the side plate 300 and the discharge casing 22. Another portion of the liquid pressurized by the impeller (1) flows into the gap between the side plate (300) and the main plate (10) of the impeller (1).

When the impeller 1 rotates, the force of the liquid (that is, fluid force) that presses the impeller 1 toward the discharge casing 22 acts on the impeller 1. Since the flow of liquid flowing into the gap between the side plate 300 and the main plate 10 is restricted by the side plate 300, the pressurized liquid flows into the gap between the side plate 300 and the main plate 10. stay in Since the liquid remaining in the gap between the side plate 300 and the main plate 10 receives the fluid force acting on the impeller 1, the movement of the impeller 1 toward the discharge casing 22 is restricted. .

When the motor pump MP operates normally, a thrust force acts on the impeller 1 from the discharge casing 22 side to the suction casing 21 side. Therefore, even if fluid force acts on the impeller 1, the impeller 1 is stably held by the bearing 5. In the embodiment shown in FIG. 50, an embodiment in which the side plate 300 is applied to the motor pump MP according to the embodiment shown in FIG. 1 has been described. However, the side plate 300 is shown in FIGS. 2 to 49. It is also applicable to the motor pump MP according to one embodiment.

Figure 51 shows another embodiment of the side plate. As shown in FIG. 51, the side plate 300 may have an opening 300a formed in its center. As described above, the liquid that flows into the gap between the side plate 300 and the main plate 10 may stay in the gap between the side plate 300 and the main plate 10.

In this case, due to the rotation of the impeller 1, the remaining liquid may rotate and soon generate heat. By forming the opening 300a in the side plate 300, the liquid between the gap between the side plate 300 and the discharge casing 22 and the gap between the side plate 300 and the impeller 1 Circulating flow is formed. Accordingly, the liquid existing between the side plate 300 and the impeller 1 flows into the discharge casing 22, preventing heat generation of the liquid, and maintaining a constant temperature of the liquid. Additionally, the opening 300a may serve to discharge air contained in the remaining liquid toward the discharge casing 22.

In the embodiment shown in FIG. 51, the opening 300a of the side plate 300 is a single opening formed on the center line CL, but the number of openings 300a is not limited to this embodiment. The side plate 300 may have a plurality of openings 300a as long as it limits the movement of the impeller 1 toward the discharge casing 22.

Additionally, the opening 300a does not necessarily need to be formed on the center line CL as long as it can form a circulating flow of liquid. For example, the side plate 300 may have at least one opening 300a arranged concentrically around the center line CL.

The shape of the opening 300a is also not particularly limited, and may have a circular shape or a polygonal shape (for example, a triangular shape or a square shape). Likewise, the size (i.e., area) of the opening 300a is not particularly limited as long as it limits movement of the side plate 300 toward the discharge casing 22.

Figure 52 is a diagram showing another embodiment of a motor pump. In the embodiment shown in Fig. 52, the motor pump MP is provided with a discharge casing 22 having a discharge port 322 extending in a vertical direction perpendicular to the center line CL direction of the motor pump MP. The discharge port 322 has a discharge port 322a that opens upward, and the suction port 21a and the discharge port 322a are orthogonal to each other.

In the embodiment shown in FIG. 52, the motor pump MP is a so-called end-top type motor pump in which the suction port 21a and the discharge port 322a are orthogonal. This motor pump MP has a compact structure. For example, depending on the installation environment of the motor pump MP, it may not be possible to install the motor pump MP having a structure in which the suction port 21a and the discharge port 22a are arranged in a straight line. Even in this case, the end-top type motor pump MP can be installed. In this way, in this embodiment, the motor pump MP can be installed in response to any installation environment.

As shown in FIG. 52, the motor pump MP may further be provided with a side plate 300 that restricts the outflow of the liquid (handling liquid) pressurized by the impeller 1 to the discharge port 322. In this way, the side plate 300 is also applicable to the end top type motor pump MP. Also, in the embodiment shown in FIG. 52, the side plate 300 may have an opening 300a (see FIG. 51).

The above-described embodiments have been described for the purpose of enabling those skilled in the art in the technical field to which the present invention pertains to practice the present invention. Various modifications to the above embodiments can naturally be made by those skilled in the art, and the technical idea of the present invention can be applied to other embodiments. Accordingly, the present invention is not limited to the described embodiments, but is to be interpreted in the widest scope according to the technical idea defined by the patent claims.

The present invention can be used in motor pumps.

1, 1A, 1B, 1C: Impeller
2: rotor
2a: iron core
2b: magnet
3: stator
3a: stator core
3b: coil
5: Bearing
6: Rotating side bearing body
6a: cylindrical part
6b: Flange part
7: Fixed side bearing body
7a: cylindrical part
7b: Flange part
10: Abacus
10a: through hole
11: side plate
11a: outer edge
12: wings
15: suction part
16: main body
17: Protrusion
17a: outer peripheral surface
17b: If you give it to me
20: stator casing
20a: If you give it to me
21: intake casing
21a: intake port
22: Discharge casing
22a: discharge port
25: Through bolt
25a: head part
30: return blade
31: Absence of seal
32, 33: Absence of seal
40, 41, 42: Home
41a: both ends
45: Load reduction structure
46: back blade
47: notch
50, 51: slope
53, 54: slope
60: inverter
61: middle casing
65: Plumbing
70, 70A, 70B: Convex portion
71: tip
75: Balance adjustment jig (center support adjustment jig)
76: Axis
77: fixture
80: Center cap
85: Balance adjustment jig (edge support adjustment jig)
86: Supporter
87: shaft
90: Weight insertion hole
91: Chu
100: control device
100a: signal receiver
100b: memory unit
100c: control unit
101: current sensor
102: terminal block
105: power line
106: signal line
107: protective cover
108: copper bar
110: cover
117: protrusion
118: Mounting part
120: Absence of seal
121: Absence of seal
125: middle casing
126: Plumbing axis
127A: Absence of seal
127B: Absence of seal
128: Discharge side bearing
129: Euro
130: Swing prevention unit
140: connection pipe
141: intake casing
141a: intake port
141b: insertion hole
142: Discharge casing
142a: discharge port
142b: Bolt receiving portion
150: fastener
160: Abacus
200: rotor holder
201: receiving part
201a: turning away
201b: Inside
201c: each side
202: Occlusion plate
203: spacer
205: Absence of seal
220: Insulating material
221: motor frame
229: seal groove
230: Inside
231: Lateral annulus
232: medial annulus
233: back part
235: protrusion
240: partition plate
241: Absence of seal
242: Through hole
245: partition plate
251: receiving part
252: Ring holder
253: Ringbu
253a: buried hole
253b: bend part
254: bending part
254a: buried hole
254b: bend part
255: main body
256: bending part
260: spacer
270: Plumbing axis
270a: tip
270b: screw hole
271: Fixed side bearing body
272: Rotating side bearing body
273: Fastener
275: middle casing
276: Liner ring
277: second bearing
280: sleeve
281: Boss Department
282: Boss Department
285, 286: collet
290: Fastener
291: spacer
300: side plate
300a: opening
322: discharge port
322a: discharge port
MP: motor pump
PU: pump unit
CL: center line
Ra: suction side area
Rb: discharge side area
Rc: middle region
RS: rotation axis
Nt:nut

Claims (23)

rotor,
a stator disposed radially outside the rotor;
a rotor holder that holds and supports the rotor;
A motor pump comprising an impeller, which is a press-molded product, to which the rotor holder is fixed. According to paragraph 1,
The rotor holder,
a press-molded annular receiving portion that accommodates the rotor;
A motor pump comprising an annular closing plate that closes the receiving portion. According to paragraph 2,
The motor pump, wherein the rotor holder has a seal member disposed between the receiving portion and the blocking plate. According to paragraph 2 or 3,
A motor pump, wherein the rotor holder is provided with a filler filled in the receiving portion. According to any one of claims 2 to 4,
The rotor holder is a motor pump having a spacer disposed between the receiving portion and the rotor. According to any one of claims 2 to 5,
The receiving part is,
lateral annulus,
and an inner annular portion disposed radially inside the outer annular portion,
A motor pump, wherein the inner annular portion has a plurality of protrusions formed at a contact portion with the rotor. According to clause 6,
The motor pump wherein the inner surface of the rotor in contact with the inner annular portion has a polygonal shape. According to any one of claims 1 to 7,
The motor pump supports the impeller and has a bearing disposed outside the passage of the impeller,
The bearing is,
A rotation side bearing body mounted on the rotor holder,
A motor pump comprising a fixed side bearing body disposed on a suction side of the rotating side bearing body. According to any one of claims 1 to 8,
The motor pump includes a stator casing that accommodates the stator and is integrally molded with a resin mold. According to clause 9,
The motor pump includes a motor frame that covers the outer peripheral surface of the stator casing and is in contact with the stator. According to any one of claims 1 to 10,
The motor pump, wherein the rotor and the bearing are disposed in a suction side area of the impeller. rotor,
a stator disposed radially outside the rotor;
a rotor holder that holds and supports the rotor;
A motor pump comprising an impeller that is a resin molded product in which the rotor holder is integrally molded. According to clause 12,
The rotor holder,
a resin molded annular accommodating portion that accommodates the rotor;
A motor pump comprising a ring holder that closes the receiving portion. According to clause 13,
The ring holder is a motor pump having an anti-rotation structure formed at a connection portion with the receiving portion. According to clause 14,
The motor pump wherein the anti-rotation structure is a buried hole in which a portion of the receiving portion is buried. According to claim 14 or 15,
The anti-rotation structure is a motor pump that is bent in the shape of the Japanese letter コ. According to any one of claims 13 to 16,
A motor pump, wherein the rotor holder has a spacer disposed between the ring holder and the rotor. According to any one of claims 13 to 17,
The ring holder is a motor pump having a plurality of protrusions formed at a contact portion with the rotor. According to any one of claims 13 to 17,
The inner surface of the rotor in contact with the ring holder has a polygonal shape. According to any one of claims 12 to 19,
The motor pump supports the impeller and has a bearing disposed outside the passage of the impeller,
The bearing is,
A rotation side bearing body mounted on the rotor holder,
A motor pump comprising a fixed side bearing body disposed on a suction side of the rotating side bearing body. According to any one of claims 12 to 20,
The motor pump includes a stator casing that accommodates the stator and is integrally molded with a resin mold. According to clause 21,
The motor pump includes a motor frame that covers the outer peripheral surface of the stator casing and is in contact with the stator. According to any one of claims 12 to 22,
The motor pump, wherein the rotor and the bearing are disposed in a suction side area of the impeller.

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